PUMP CHAMBER STRUCTURES AND DIAPHRAGM PUMPS

Disclosed herein are a pump chamber structure and a diaphragm pump. The diaphragm pump includes a pump housing, an air inlet assembly, an air outlet assembly, a plurality of diaphragm structures, and a plurality of pump covers. The pump housing includes a plurality of shell plates and a side plate, the plurality of shell plates are sequentially connected along a circumferential direction of the pump housing and together with the side plate enclose a pump chamber, and each of the plurality of shell plates is provided with chamber openings extending therethrough for communicating with the pump chamber. The air inlet assembly and the air outlet assembly are disposed on the side plate and spaced apart from each other. The plurality of diaphragm structures are disposed on the chamber openings in a one-to-one correspondence, and a peripheral edge of each of the plurality of diaphragm structures is connected and fixed to the corresponding chamber opening. The plurality of pump covers are disposed to cover openings of the chamber openings in a one-to-one correspondence, and each pump cover, the corresponding shell plate, and the corresponding diaphragm structure collectively define a working chamber. Each of the plurality of pump covers is provided with an air inlet hole and an air outlet hole, and the air inlet hole and the air outlet hole on the same pump cover are spaced apart along a circumferential direction of the pump cover.

Skip to: Description  ·  Claims  · Patent History  ·  Patent History
Description
CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a Continuation-in-part of International Application No. PCT/CN 2026/077816, filed on Feb. 9, 2026, which claims priority to Chinese Patent Application No. 202520315517.3, filed on Feb. 26, 2025, Chinese Patent Application No. 202520314671.9, filed on Feb. 26, 2025, Chinese Patent Application No. 202520314679.5, filed on Feb. 26, 2025, Chinese Patent Application No. 202510276879.0, filed on Mar. 10, 2025, and Chinese Patent Application No. 202520409927.4, filed on Mar. 10, 2025, the entire contents of each of which are hereby incorporated by reference.

TECHNICAL FIELD

The present disclosure relates to the field of diaphragm pump technology, and in particular to a pump chamber structure and a diaphragm pump.

BACKGROUND

A diaphragm pump is a type of transport pump that relies on a movement of a diaphragm to transport a liquid or gas medium. A working chamber is formed between a diaphragm sheet and a pump cover. Through a reciprocating movement of the diaphragm sheet, a volume of the working chamber changes, thereby achieving suction and discharge of the medium. An air outlet and an air inlet are provided at each diaphragm sheet, the air outlet is connected to an air outlet fluid line, and the air inlet is connected to an air inlet fluid line, so as to achieve suction and discharge of gas at the diaphragm sheet. Since each side of a chamber body is provided with the diaphragm sheet and the pump cover, the arrangement of fluid lines on the diaphragm pump tends to be disordered, thereby increasing an overall volume of the diaphragm pump.

Therefore, it is necessary to provide a pump chamber structure and a diaphragm pump, so as to achieve a compact overall structure, orderly fluid lines, and a reduced volume.

SUMMARY

One or more embodiments of the present disclosure provide a diaphragm pump. The diaphragm pump includes a pump housing, an air inlet assembly, an air outlet assembly, a plurality of diaphragm structures, and a plurality of pump covers. The pump housing includes a plurality of shell plates and a side plate, the plurality of shell plates are sequentially connected along a circumferential direction of the pump housing and together with the side plate enclose a pump chamber, each of the plurality of shell plates is provided with chamber openings extending therethrough for communicating with the pump chamber. The air inlet assembly and the air outlet assembly are disposed on the side plate and spaced apart from each other. The plurality of diaphragm structures are disposed on the chamber openings in a one-to-one correspondence, a peripheral edge of each of the plurality of diaphragm structures is connected and fixed to the corresponding chamber opening. The plurality of pump covers are disposed to cover openings of the chamber openings in a one-to-one correspondence, each pump cover, the corresponding shell plate, and the corresponding diaphragm structure collectively define a working chamber, each of the plurality of pump covers is provided with an air inlet hole and an air outlet hole. The air inlet hole and the air outlet hole on the same pump cover are spaced apart along a circumferential direction of the pump cover; the air inlet hole and the air outlet hole of each pump cover are in communication with the air inlet assembly and the air outlet assembly, respectively. The air inlet holes on a plurality of pump covers located on the same shell plate are spaced apart along an axial direction of the pump covers, and the air outlet holes on the plurality of pump covers located on the same shell plate are spaced apart along the axial direction of the pump covers.

One or more embodiments of the present disclosure provide a pump chamber structure for a diaphragm pump. The pump chamber structure includes a chamber body, a plurality of pump covers, a pump shaft, and a plurality of transmission components. The chamber body is hollow and has a plurality of peripheral sidewalls sequentially connected along a circumferential direction of the chamber body, each of the plurality of peripheral sidewalls is provided with chamber openings, and the chamber openings on the two peripheral sidewalls disposed opposite to each other are arranged opposite to each other. The plurality of pump covers are disposed to cover the plurality of chamber openings in a one-to-one correspondence. The pump shaft at least partially extends through the chamber body. The plurality of transmission components are sequentially disposed within the chamber body along an axial direction of the pump shaft. One end of each of the plurality of transmission components is rotatably connected to the pump shaft, and the other end of each of the plurality of transmission components is disposed to cover the corresponding chamber opening and collectively defines a working chamber together with the corresponding pump cover. And the plurality of transmission components are structurally identical.

One or more embodiments of the present disclosure provide a pump chamber structure for a diaphragm pump. The pump chamber structure includes a chamber housing, a pump shaft, and a plurality of sets of connecting rod assemblies. The chamber housing has a plurality of peripheral side surfaces, each of the plurality of peripheral side surfaces is provided with at least one chamber opening. The pump shaft is disposed within the chamber housing along an axial direction of the chamber housing. The plurality of sets of connecting rod assemblies are arranged side by side within the chamber housing along the axial direction of the pump shaft. One end of each set of the plurality of sets of connecting rod assemblies is sleeved on an outer peripheral side of the pump shaft, and the other end of each set of the plurality of sets of connecting rod assemblies extends into the corresponding chamber opening. The chamber housing is provided with a plurality of limiting portions, an end of each set of the plurality of sets of connecting rod assemblies extending into the chamber opening is provided with a mating portion, and the limiting portion cooperates with the corresponding mating portion to limit movement of the corresponding connecting rod assembly along the axial direction of the pump shaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram illustrating a structure of a diaphragm pump according to some embodiments of the present disclosure;

FIG. 2 is a schematic diagram illustrating the diaphragm pump of FIG. 1 from another perspective according to some embodiments of the present disclosure;

FIG. 3 is a schematic diagram illustrating piping connections in a diaphragm pump according to some embodiments of the present disclosure;

FIG. 4 is a schematic diagram illustrating piping connections in a diaphragm pump according to other embodiments of the present disclosure;

FIG. 5 is a cross-sectional view illustrating the diaphragm pump of FIG. 1 according to some embodiments of the present disclosure;

FIG. 6 is a schematic diagram illustrating a diaphragm structure of FIG. 5 according to some embodiments of the present disclosure;

FIG. 7 is a cross-sectional view illustrating the diaphragm structure of FIG. 6 according to some embodiments of the present disclosure;

FIG. 8 is a schematic diagram illustrating an interface structure of FIG. 1 according to some embodiments of the present disclosure;

FIG. 9 is a cross-sectional view illustrating the interface structure of FIG. 8 according to some embodiments of the present disclosure;

FIG. 10 is a schematic diagram illustrating a structure of a diaphragm pump according to other embodiments of the present disclosure;

FIG. 11 is a schematic diagram illustrating the diaphragm pump of FIG. 10 according to some embodiments of the present disclosure;

FIG. 12 is a schematic diagram illustrating the diaphragm pump of FIG. 11 from another perspective according to some embodiments of the present disclosure;

FIG. 13 is a schematic diagram illustrating the diaphragm pump of FIG. 10 according to other embodiments of the present disclosure;

FIG. 14 is a schematic diagram illustrating a pump cover according to some embodiments of the present disclosure;

FIG. 15 is a schematic diagram illustrating a structure of a diaphragm pump according to yet other embodiments of the present disclosure;

FIG. 16 is a schematic cross-sectional structural diagram illustrating the diaphragm pump of FIG. 15 according to some embodiments of the present disclosure;

FIG. 17 is an enlarged schematic cross-sectional structural diagram illustrating a diaphragm sheet and a pump cover of FIG. 15 according to some embodiments of the present disclosure;

FIG. 18 is a schematic cross-sectional structural diagram illustrating the diaphragm pump of FIG. 15 according to other embodiments of the present disclosure;

FIG. 19 is a schematic diagram illustrating a structure of an eccentric member of FIG. 15 according to some embodiments of the present disclosure;

FIG. 20 is a schematic diagram illustrating a structure of a pump chamber structure according to some embodiments of the present disclosure;

FIG. 21 is an exploded schematic structural diagram illustrating the pump chamber structure of FIG. 20 according to some embodiments of the present disclosure;

FIG. 22 is a schematic cross-sectional structural diagram illustrating the pump chamber structure of FIG. 20 according to some embodiments of the present disclosure;

FIG. 23 is an enlarged schematic structural diagram illustrating detail A of FIG. 22 according to some embodiments of the present disclosure; and

FIG. 24 is a schematic diagram illustrating a structure of a diaphragm pump according to still other embodiments of the present disclosure.

 DETAILED DESCRIPTION

The technical solutions of the present disclosure will be clearly and completely described below with reference to the accompanying drawings. It is apparent that the described embodiments are merely some embodiments of the present disclosure, rather than all possible embodiments. The present disclosure will be described in detail below with reference to the accompanying drawings and in conjunction with the embodiments. It should be noted that, where there is no conflict, the embodiments in the present disclosure and the features in the embodiments may be combined with each other.

In the embodiments of the present disclosure, the term “and/or” describes an association relationship of associated objects, which means that three relationships may exist. For example, “A and/or B” may represent the following three situations: A exists alone, both A and B exist, and B exists alone. The character “/” generally indicates that the associated objects before and after it have an “or” relationship.

It should be noted that the terms “first”, “second”, or the like used in the specification, claims, and accompanying drawings of the present disclosure are intended to distinguish between similar objects and are not intended to specify a particular order or sequence.

In the embodiments of the present disclosure, the term “a plurality of” refers to two or more, and other quantifiers are similar thereto.

In the present disclosure, unless otherwise specified, directional terms such as “upper” “lower”, “top”, and “bottom” are generally used with respect to the directions shown in the accompanying drawings, or with respect to the component itself in a vertical, perpendicular, or gravity direction; similarly, for ease of understanding and description, “inner” and “outer” refer to the inner and outer sides relative to the contours of the respective components, but the above-mentioned directional terms are not intended to limit the present disclosure.

To make the objectives, technical solutions, and advantages of the embodiments of the present disclosure clearer, the various embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. However, those skilled in the art may understand that, in the various embodiments of the present disclosure, many technical details are set forth to enable readers to better understand the present disclosure. However, even without these technical details and various changes and modifications based on the following embodiments, the technical solutions claimed in the present disclosure may also be implemented. A division of the following embodiments is for ease of description, and should not constitute any limitation on specific implementation manners of the present disclosure. The various embodiments may be combined with each other and referenced to each other, provided that there is no conflict.

FIG. 1 is a schematic diagram illustrating a structure of a diaphragm pump according to some embodiments of the present disclosure. FIG. 2 is a schematic diagram illustrating the diaphragm pump of FIG. 1 from another perspective according to some embodiments of the present disclosure. FIG. 3 is a schematic diagram illustrating piping connections in the diaphragm pump according to some embodiments of the present disclosure. FIG. 4 is a schematic diagram illustrating the piping connections in the diaphragm pump according to other embodiments of the present disclosure.

The present disclosure provides a diaphragm pump 100a. As shown in FIGS. 1 to 4, the diaphragm pump 100a includes a pump housing 1a, an air inlet assembly 21a, an air outlet assembly 22a, and a plurality of pump covers 3a. The pump housing 1a includes a plurality of shell plates 11a, such as at least four shell plates 11a. The at least four shell plates 11a include a first shell plate 111a, a second shell plate 112a, a third shell plate 113a, and a fourth shell plate 114a. The at least four shell plates 11a are sequentially connected along a circumferential direction of the pump housing 1a and together with the side plate 12a enclose a pump chamber. Each of the at least four shell plates 11a is provided with chamber openings 13a extending therethrough for communicating with the pump chamber (More descriptions regarding the chamber openings 13a may be found elsewhere in the present disclosure (e.g., FIG. 5 and related descriptions thereof)). The air inlet assembly 21a and the air outlet assembly 22a are disposed on the side plate 12a and spaced apart from each other. The plurality of pump covers 3a include a first pump cover 31a and a second pump cover 32a located on the first shell plate 111a; a third pump cover 33a and a fourth pump cover 34a located on the second shell plate 112a; a fifth pump cover 35a and a sixth pump cover 36a located on the third shell plate 113a; and a seventh pump cover 37a and an eighth pump cover 38a located on the fourth shell plate 114a. Each of the plurality of pump covers 3a is provided with an air inlet hole 391a and an air outlet hole 392a. The air inlet hole 391a of the first pump cover 31a and the air inlet hole 391a of the second pump cover 32a are connected in parallel, the air inlet hole 391a of the third pump cover 33a and the air inlet hole 391a of the fourth pump cover 34a are connected in parallel, the air inlet hole 391a of the fifth pump cover 35a and the air inlet hole 391a of the sixth pump cover 36a are connected in parallel, and three parallel groups are connected to the air inlet assembly 21a, respectively; the air outlet holes 392a of the first pump cover 31a, the second pump cover 32a, the third pump cover 33a, the fourth pump cover 34a, the fifth pump cover 35a, and the sixth pump cover 36a are connected in parallel to form a first-stage fluid line 41a,and the air inlet hole 391a and the air outlet hole 392a of the seventh pump cover 37a and the air inlet hole 391a and the air outlet hole 392a of the eighth pump cover 38a are connected in series with the first-stage fluid line 41a, after being connected in parallel or in series with each other.

The pump housing 1a refers to a main housing of the entire diaphragm pump 100a, including the plurality of shell plates 11a and the side plate 12a, and defining therein the pump chamber for accommodating fluid and diaphragms. In some embodiments, a material of the pump housing 1a may be metal (e.g., stainless steel, aluminum alloy), plastic (e.g., polypropylene, nylon), or the like.

The pump chamber refers to the overall enclosed space inside the pump housing 1a.

The shell plates 11a refer to a plurality of plate-shaped components that form a peripheral sidewall of the pump housing 1a.

The side plate 12a refers to an end face cover plate of the pump housing 1a, configured to enclose an end of the pump housing 1a and to mount the air inlet assembly and the air outlet assembly.

In some embodiments, the plurality of shell plates 11a and the side plate 12a may form the pump housing 1a in a plurality of manners, such as by splicing or integral molding.

The chamber openings 13a refer to through holes provided on the shell plates 11a. In some embodiments, the chamber opening 13a may have a plurality of shapes, such as a circular shape, a special shape, or the like.

FIG. 5 is a cross-sectional view illustrating the diaphragm pump in FIG. 1 according to some embodiments of the present disclosure. FIG. 6 is a schematic diagram illustrating a diaphragm structure of FIG. 5 according to some embodiments of the present disclosure. FIG. 7 is a cross-sectional view illustrating the diaphragm structure of FIG. 6 according to other embodiments of the present disclosure.

In some embodiments, as shown in FIGS. 5 to 7, the diaphragm pump 100a includes a plurality of diaphragm structures 5a, and the plurality of diaphragm structures 5a are disposed on the chamber openings 13a in a one-to-one correspondence. The chamber openings 13a on each shell plate 11a are spaced apart along an axial direction of the shell plate 11a.

The diaphragm structures 5a are core working components of the diaphragm pump 100a, which change a volume of the pump chamber by reciprocating pulsation, thereby facilitating the intake and discharge of gas. In some embodiments, the diaphragm structures 5a may be made of a flexible material (e.g., rubber, plastic, or a metal film).

The term “spaced apart along the axial direction” refers to that, on the same shell plate, the chamber openings 13a are sequentially arranged along a central axis direction of the pump housing 1a, and projections thereof in the axial direction do not overlap with each other.

In some embodiments, each of the plurality of diaphragm structures 5a includes a diaphragm body 51a and an outwardly turned flange 52a. The outwardly turned flange 52a is formed by bending and extending from a periphery of the diaphragm body 51a along an axial direction of the diaphragm body 51a. The diaphragm body 51a and the outwardly turned flange 52a are an integral structure, and an outer diameter of the integral structure is in a range of 104.5 mm to 105.5 mm. The outwardly turned flange 52a is configured to be inserted into the chamber opening 13a, a width of the outwardly turned flange 52a along a radial direction of the diaphragm body 51a matches a width of the chamber opening 13a, and the width of the outwardly turned flange 52a along the radial direction of the diaphragm body 51a is in a range of 4.2 mm to 5.25 mm.

The diaphragm body 51a refers to a main body portion of the diaphragm structure 5a, such as a circular flexible film sheet.

The outwardly turned flange 52a refers to an annular flange structure extending from a peripheral edge of the diaphragm body 51a.

The outer diameter of the integral structure refers to the maximum circular contour diameter of the integral structure formed by the diaphragm body 51a and the outwardly turned flange 52a (i.e., the outer edge diameter of the outwardly turned flange 52a). In some embodiments, as shown in FIG. 7, the outer diameter of the integral structure may be represented by D, and satisfies 104.5 mm≤D≤105.5 mm. For example, the outer diameter of the integral structure may be 104.5 mm, 105 mm, 105.5 mm, or the like.

It may be understood that, in the present disclosure, the term “radial direction” refers to a direction perpendicular to a central axis of the diaphragm pump and a direction parallel thereto.

The width of the outwardly turned flange 52a along the radial direction of the diaphragm body 51a refers to a radial distance from a connecting root of the diaphragm body 51a and the outwardly turned flange 52a (i.e., a peripheral edge of the diaphragm body 51a) to an outer edge of the outwardly turned flange 52a.

By providing the outwardly turned flange, when the diaphragm structures for the diaphragm pump are mounted, since the corresponding positions of the diaphragm pump are provided with the chamber openings, and the chamber openings are provided with grooves, the outwardly turned flange can be accommodated in the grooves and then pressed from upper and lower sides. On the one hand, the configuration can prevent the diaphragm structures for the diaphragm pump from disengaging; on the other hand, a plug-in connection of the outwardly turned flange facilitates easy mounting and removal. By limiting the outer diameter of the integral structure formed by the diaphragm body and the outwardly turned flange, when the outwardly turned flange is mounted in the groove, the outwardly turned flange can be just engaged in the groove on the chamber opening.

In some embodiments, the outwardly turned flange 52a may be bent and extended integrally from the periphery of the diaphragm body 51a along the axial direction, i.e., the outwardly turned flange 52a extends along the axial direction and has a constant outer diameter; or alternatively, the outwardly turned flange 52a may be configured to taper along the axial direction. In the present embodiment, the outwardly turned flange 52a is bent and extended integrally from the periphery of the diaphragm body 51a along the axial direction and has a consistent overall outer diameter.

If the outer diameter of the integral structure formed by the diaphragm body 51a and the outwardly turned flange 52a is excessively large, mounting of the outwardly turned flange 52a into the groove on the chamber opening 13a may be hindered. Conversely, if the outer diameter of the integral structure formed by the diaphragm body 51a and the outwardly turned flange 52a is excessively small, when the diaphragm structure 5a is mounted in the groove on the chamber opening 13a, the sealing performance between the outwardly turned flange 52a and an inner wall of the groove of the chamber opening 13a may be compromised, and the mounting stability may be adversely affected, rendering the diaphragm structure prone to displacement.

In some embodiments, the shape of the outwardly turned flange 52a may match the inner wall of the groove of the chamber opening 13a. In the present embodiment, as shown in FIG. 7, the width of the outwardly turned flange 52a along the radial direction isH, with 4.2 mm≤H≤5.25 mm. For example, the width of the outwardly turned flange 52a along the radial direction of the diaphragm body 51a may be 4.2 mm, 4.7 mm, 5.25 mm, or the like. In some embodiments, when the width of the outwardly turned flange 52a along the radial direction is greater than 5.25 mm, the outwardly turned flange 52a may be unable to be mounted in the groove of the chamber opening 13a; when the width of the outwardly turned flange 52a along the radial direction is less than 4.2 mm, after the outwardly turned flange 52a is mounted in the groove of the chamber opening 13a, insufficient sealing may result, or problems such as easy displacement may occur.

An end edge of the outwardly turned flange 52a has an abutting portion 521a configured to abut an inner wall of the chamber opening 13a, such that the abutting portion 521a is in sealing abutment with the inner wall of the chamber opening 13a. The abutting portion 521a may be formed in a plurality of shapes, e.g., square, arcuate, triangular, etc.

Taking the abutting portion 521a being square as an example, the outwardly turned flange 52a may be provided with an overall square structure, and the square structure abuts the inner wall of the chamber opening 13a to form a seal. Alternatively, the outwardly turned flange 52a may also be provided with a plurality of square structures spaced apart along the radial direction, each of the plurality of square structures abuts the inner wall of the chamber opening 13a to form a seal. At this time, the plurality of square structures form a plurality of sealing regions, which may effectively improve sealing reliability.

In other embodiments, the abutting portions 521a may include a plurality of different shapes, and a plurality of abutting portions 521a of different shapes are spaced apart along the radial direction.

In some embodiments, a supporting member 53a is mounted at a middle position of the diaphragm body 51a. The supporting member 53a extends along an axial direction. An outer surface of the supporting member 53a is provided with an external thread, thereby allowing connection to other components via the external thread. In some embodiments, the diaphragm body 51a has a first surface 511a located on the same side as the outwardly turned flange 52a. A mounting boss 512a is formed on the first surface 511a by protruding outward from a central portion thereof, and the supporting member 53a is mounted on the mounting boss 512a. In other embodiments, the supporting member 53a may also be provided with an internal thread hole along the axial direction, allowing connection to other components via an internal thread within the internal thread hole.

The mounting boss 512a refers to a solid protruding connection portion on a surface of the diaphragm structure 5a.

In some embodiments, the mounting boss 512a extends axially from the first surface 511a and is configured to taper along the axial direction. The mounting boss 512a is configured as a conical structure, which can ensure reliable and stable connection of the supporting member 53a. In addition, the conical structure has an arcuate outer surface, thereby reducing interference with other components.

In some embodiments, to further improve the reliability and stability of the supporting member 53a and to increase the connection reliability, an outer surface of the mounting boss 512a is provided with a plurality of first reinforcing ribs 5121a, and each of the plurality of first reinforcing ribs 5121a extends along a radial direction on a surface of the mounting boss 512a. The plurality of first reinforcing ribs 5121a are spaced apart along a circumferential direction of the mounting boss 512a.

Taking the mounting boss 512a being in a conical structure as an example, one end of each of the plurality of first reinforcing ribs 5121a is located proximate to the top of the conical structure, and the other end of each of the plurality of first reinforcing ribs 5121a is located proximate to the bottom of the conical structure.

In some embodiments, the first surface 511a has a second reinforcing rib 5122a at the position between the mounting boss 512a and the outwardly turned flange 52a, and the second reinforcing rib 5122a extends along a circumferential direction. To further improve the strength, the first surface 511a has a plurality of third reinforcing ribs 513a at the position between the mounting boss 512a and the outwardly turned flange 52a, and the plurality of third reinforcing ribs 513a extend along a radial direction and are spaced apart along a circumferential direction.

The air inlet assembly 21a and the air outlet assembly 22a refer to total air inlet and total air outlet interfaces mounted on the side plate 12a, configured to connect to an external fluid line. In some embodiments, materials of the air inlet assembly 21a and the air outlet assembly 22a may be metal (e.g., stainless steel), ceramic, or the like.

FIG. 8 is a schematic diagram illustrating an interface structure of FIG. 1 according to some embodiments of the present disclosure. FIG. 9 is a cross-sectional view illustrating the interface structure of FIG. 8 according to some embodiments of the present disclosure.

In some embodiments, as shown in FIGS. 8 and 9, at least one of the air inlet assembly 21a or the air outlet assembly 22a is the interface structure 23a. The interface structure 23a includes a cylindrical body 231a, the cylindrical body 231a is provided with a through air hole 2311a extending therethrough along an axial direction thereof, one end of the through air hole 2311a is a closed end, and the other end of the through air hole 2311a is an open end. The cylindrical body 231a is further provided with a plurality of branch air holes 2312a extending therethrough, the plurality of branch air holes 2312a are in communication with the through air hole 2311a, and the open end is connected to a fluid line.

The interface structure 23a refers to a gas distribution/collection joint integrating a plurality of air channels.

The cylindrical body 231a refers to a main portion of the interface structure 23a, and is in a cylindrical shape (columnar).

The through air hole 2311a refers to a central passage extending through the cylindrical body 231a along an axial direction.

The branch air holes 2312a refer to a plurality of through-holes (radial holes) formed on a sidewall of the cylindrical body 231a.

The branch air holes 2312a are in communication with the through air hole 2311a, configured to distribute gas to different pump covers (when intaking air) or collect gas from different pump covers (when exhausting air).

The fluid line refers to a hollow conduit connected between the open end of the air inlet assembly 21a or the air outlet assembly 22a and external equipment, configured to deliver gas to the diaphragm pump 100a or guide gas exhausted from the diaphragm pump 100a to a target position. In some embodiments, a detachable connection and sealing between the fluid line and the open end is achieved by a threaded connection or a snap-fit connection.

By providing the interface structure, the air inlet assembly and the air outlet assembly of the diaphragm pump can both use the interface structure. Each interface structure includes the cylindrical body. The cylindrical body is provided with the through air hole along the axial direction thereof, and the through air hole has the closed end and the open end located at two ends thereof. The cylindrical body is further provided with the plurality of branch air holes extending therethrough. The plurality of branch air holes are in communication with the through air hole, and the open end of the through air hole is configured to be connected to the fluid line by at least one of a threaded connection or a snap-fit connection, so that the air inlet assembly and the air outlet assembly need not be disposed on two opposite sides of the diaphragm pump.

In some embodiments, the interface structure 23a may be connected to other fluid lines via internal and external threads. In some embodiments, an outer wall of the open end is provided with an external thread, or an inner wall of the open end is provided with an internal thread. In the present embodiment, the inner wall of the open end of the through air hole 2311a is provided with the internal thread. By providing the internal thread on the inner wall of the open end of the through air hole 2311a, the outer wall of the open end may also be connected through other manners (e.g., a snap-fit connection), thereby allowing selection according to specific needs.

In other embodiments, the cylindrical body 231a is recessed inward at an outer wall surface of the open end to form a mounting step 232a. The mounting step 232a has a recessed wall surface 2321a proximate to the outer wall surface of the open end and a step surface 2322a connected to the recessed wall surface 2321a. The interface structure 23a further includes a clamping member 233a, and the clamping member 233a is sleeved on the recessed wall surface 2321a and supported on the step surface 2322a.

The mounting step 232a refers to a stepped structure formed due to the inward recessing of the outer wall surface.

The recessed wall surface 2321a refers to a new outer cylindrical surface formed by inward recessing, located on the side proximate to the open end and having a diameter smaller than that of an original outer wall surface.

The step surface 2322a refers to an annular transition surface connecting the original outer wall surface and the recessed wall surface.

In some embodiments, the recessed wall surface 2321a and the step surface 2322a are integrally formed.

The clamping member 233a includes a clamping ring, a clamping sleeve, a quick-connect joint housing, or the like.

The pump covers 3a refer to covers configured to cover outer ends of the chamber openings 13a. In some embodiments, the pump covers 3a may have a plurality of shapes, such as a square shape, a circular shape, or the like. Materials of the pump covers 3a may be metal (e.g., grey cast iron, ductile cast iron, or stainless steel), plastic (e.g., polypropylene, polyvinylidene fluoride, or polytetrafluoroethylene), or the like.

The air inlet hole 391a and the air outlet hole 392a respectively refer to a gas inlet and an outlet of the pump cover 3a.

The parallel connection refers to a configuration in which a plurality of holes are in fluid communication with the same fluid line, have the same pressure, and are capable of simultaneous air intake or exhaust.

The series connection refers to a configuration in which an outlet of a preceding stage is connected to an inlet of a succeeding stage, such that gas flows through the stages sequentially, the total pressure drop is accumulated, and the flow rate is the same across the stages.

It should be understood that, in the present disclosure, the term “axial direction” refers to a direction perpendicular to the side plate and parallel to a central axis of the pump housing (i.e., a length direction of the diaphragm pump, from the side plate to the opposite end), and the term “circumferential direction” refers to a circumferential direction around the central axis of the pump housing (i.e., a direction of rotation around the axis, perpendicular to the axial direction).

In some embodiments, the air inlet assembly 21a includes a plurality of air inlets; the air inlet hole 391a of the first pump cover 31a and the air inlet hole 391a of the second pump cover 32a are connected in parallel and then connected to one of the air inlets; the air inlet hole 391a of the third pump cover 33a and the air inlet hole 391a of the fourth pump cover 34a are connected in parallel and then connected to yet another of the air inlets; and the air inlet hole 391a of the fifth pump cover 35a and the air inlet hole 391a of the sixth pump cover 36a are connected in parallel and then connected to another of the air inlets.

In the present embodiment, a count of the air inlets is three. In other embodiments, the count of the air inlets may also be four, five, or the like, and may be determined according to specific needs. Merely by way of example, the count of the air inlets may be determined according to a count of the chambers of the diaphragm pump 100a. For example, for a four-chamber configuration, the count of the air inlets is three; for a five-chamber configuration, the count of the air inlets is four.

The air inlets of the air inlet assembly 21a are spaced apart along the axial direction and the circumferential direction. The air inlet holes 391a of the pump covers 3a located on the same shell plate 11a are connected to the same air inlet, and the air inlet holes 391a of the pump covers 3a located on the same shell plate 11a are spaced apart along the axial direction, thereby forming a staggered arrangement of fluid lines and a more reasonable layout.

The air inlets are spaced apart along the axial direction, i.e., the plurality of air inlets are successively spaced apart along the axial direction (e.g., one proximate to the side plate, another further inward, and a third further inward). The air inlets are not on a same cross-section, thereby avoiding overlapping of the fluid lines along the axial direction.

The air inlets are spaced apart along the circumferential direction, i.e., the plurality of air inlets are staggered in angle along the circumferential direction (e.g., a first air inlet is oriented towards 0 °, a second is oriented towards 120 °, and a third is oriented towards 240 °). The air inlets are not at a same angle, thereby avoiding stacking of the fluid lines at a same orientation.

In some embodiments, on the same shell plate 11a, the air inlet holes of two pump covers 3a are not arranged side by side at a same axial position. Instead, one is positioned closer to the side plate 12a, and the other is positioned farther away from the side plate 12a, so that even on the same shell plate 11a, the air inlet fluid lines of the two pump covers 3a do not overlap along the axial direction, thereby facilitating wiring and connector mounting.

In some embodiments, a plurality of connection manners may exist among the air inlet holes 391a of the plurality of pump covers 3a.

In a first connection manner, with reference to FIG. 3, the air inlet hole 391a of the first pump cover 31a and the air inlet hole 391a of the second pump cover 32a are connected in parallel to form a first branch; the air inlet hole 391a of the third pump cover 33a and the air inlet hole 391a of the fourth pump cover 34a are connected in parallel to form a second branch; the air inlet hole 391a of the fifth pump cover 35a and the air inlet hole 391a of the sixth pump cover 36a are connected in parallel to form a third branch; and the first branch, the second branch, and the third branch are connected to the air inlet assembly 21a, respectively. The air outlet holes 392a of the first pump cover 31a, the second pump cover 32a, the third pump cover 33a, the fourth pump cover 34a, the fifth pump cover 35a, and the sixth pump cover 36a are all connected in parallel to form the first-stage fluid line 41a; the air inlet holes 391a and the air outlet holes 392a of the seventh pump cover 37a and the eighth pump cover 38a are connected in parallel to form the second-stage fluid line 42a; and the first-stage fluid line 41a and the second-stage fluid line 42a are connected in series to form a two-stage fluid line.

It may be understood that, the air inlet holes 391a and the air outlet holes 392a of the seventh pump cover 37a and the eighth pump cover 38a are connected in parallel, respectively (i.e., the two air inlet holes are in communication, and the two air outlet holes are in communication).

The two-stage fluid line refers to a complete two-stage air path system formed by the first-stage fluid line and the second-stage fluid line connected in series.

Taking the air inlet assembly 21a including a first air inlet 211a, a second air inlet 212a, and a third air inlet 213a as an example, the first branch, the second branch, and the third branch are connected to the first air inlet 211a, the second air inlet 212a, and the third air inlet 213a, respectively. In some embodiments, the first air inlet 211a, the second air inlet 212a, and the third air inlet 213a are spaced apart along the axial direction, thereby allowing the arrangement of the fluid line to be more orderly and avoiding problems such as entanglement, or the like.

In a second connection manner, with reference to FIG. 4, the air inlet holes 391a of the first pump cover 31a and the second pump cover 32a are connected in parallel to form a first branch; the air inlet holes 391a of the third pump cover 33a and the fourth pump cover 34a are connected in parallel to form a second branch; the air inlet holes 391a of the fifth pump cover 35a and the sixth pump cover 36a are connected in parallel to form a third branch; and the first branch, the second branch, and the third branch are connected to the air inlet assembly 21a, respectively. The air outlet holes 392a of the first pump cover 31a, the second pump cover 32a, the third pump cover 33a, the fourth pump cover 34a, the fifth pump cover 35a, and the sixth pump cover 36a are all connected in parallel to form the first-stage fluid line 41a; the air inlet hole 391a of the seventh pump cover 37a and the air outlet hole 392a of the seventh pump cover 37a are connected in series to form the second-stage fluid line 42a; the air inlet hole 391a of the eighth pump cover 38a and the air outlet hole 392a of the eighth pump cover 38a are connected in series to form a third-stage fluid line 43a; and the first-stage fluid line 41a,the second-stage fluid line 42a,and the third-stage fluid line 43a are connected in series to form a three-stage fluid line.

It may be understood that, the count of the shell plates in the diaphragm pump 100a may also be five, six, or even more. Correspondingly, a four-stage fluid line, a five-stage fluid line, or the like may also be formed.

Through a setting of an internal structure of the diaphragm pump, an adjustment of a multi-stage connection manner of the diaphragm pump may be achieved for achieving power grading.

In some embodiments, the diaphragm pump also includes a sensor 6a and a controller 7a. The plurality of diaphragm structures have the conical mounting boss 512a, and the first reinforcing ribs 5121a are provided on the mounting boss 512a. The first reinforcing ribs 5121a are heat pipe structures. And the sensor 6a is configured to detect a stress of the plurality of shell plates, and in response to the stress exceeding a stress threshold, cut off power or adjust an air inlet pressure.

The sensor 6a refers to a physical component configured to detect deformation of the shell plate 11a under force and output an electrical signal.

In some embodiments, the first reinforcing ribs 5121a are the heat pipe structures, each of which is hollow inside and filled with a heat transfer fluid (such as an alcohol-based fluid, or a refrigerant (e.g., R134a, R32, or the like)), and efficiently transfers heat by utilizing a phase change principle.

In some embodiments, when manufacturing the diaphragm structure 5a, the hollow first reinforcing rib 5121a is adhered to a surface of the conical mounting boss 512a, and one end of the first reinforcing rib 5121a is fixed to the mounting boss, while the other end extends outward to an outside of the pump housing 1a and forms thermal contact with an outer casing heat sink. During manufacturing, after the heat transfer fluid is injected into the internal cavity of the first reinforcing rib 5121a, the first reinforcing rib 5121a is then sealed.

The outer casing heat sink refers to a heat-conducting fin structure disposed on an outside of the pump housing of the diaphragm pump. In some embodiments, a material of the outer casing heat sink is metal, such as an aluminum alloy or a copper alloy.

When the chambers of the diaphragm pump 100a compress gas and generate heat, the heat is transferred to the mounting boss 512a, thereby causing the heat transfer fluid inside the first reinforcing rib 5121a located thereat to be heated and evaporate into a gas. The gas flows along the internal cavity of the first reinforcing rib 5121a towards a condensation region located at one end of the outer casing heat sink, and liquefies after encountering cold, thereby releasing the carried heat. The liquefied heat transfer fluid flows back to the mounting boss 512a through capillary action or gravity, forming a continuous heat circulation loop.

The controller 7a may process the data and/or the information obtained from other devices (e.g., a sensor). The controller 7a may execute program instructions based on the data, the information, and/or processing results to execute one or more functions described in the present disclosure. In some embodiments, the controller 7a may include one or more sub-processing devices (e.g., a single-core processing device or a multi-core, multi-chip processing device). Merely by way of example, the controller 7a may include a Central Processing Unit (CPU), an Application-Specific Integrated Circuit (ASIC), a microprocessor, or the like, or any combination thereof.

The stress refers to a stress value corresponding to micro-deformation generated in the shell plate 11a under an internal gas pressure or a mechanical transmission action. In some embodiments, the stress may be detected and obtained by the sensor 6a.

The stress threshold refers to a preset safe critical stress value characterizing an existing risk of permanent plastic deformation or rupture in the shell plate. In some embodiments, the stress threshold may be set based on actual needs and stored in the controller.

The air inlet pressure refers to a gas pressure at the air inlet assembly 21a of the diaphragm pump, i.e., a supply pressure when an external gas source conveys gas into the pump.

In some embodiments, the controller 7a reads in real time the stress value collected by the sensor 6a and compares it with the stress threshold. When the real-time stress is greater than or equal to the stress threshold, the controller 7a executes one or both of the following protective actions: cutting off motor power: the controller 7a sends a disconnect signal to a relay, and the relay operates to cut off a power supply line of a drive motor, thereby causing the drive motor to stop operating and preventing the stress from further increasing; adjusting the air inlet pressure: the controller 7a sends a control signal to an electric valve on an air inlet line, and the electric valve reduces an opening degree of an internal channel based on the signal, thereby reducing an amount of gas entering the pump chamber, so as to reduce the air inlet pressure and bring the stress of the shell plate back to a safe range.

In some embodiments, with reference to FIG. 5, a limiting groove 131a is provided at the chamber opening 13a, and the diaphragm structure 5a includes an engagement protrusion 54a. The diaphragm pump 100a further includes an electronic proportional valve 8a and a multimodal sensor 9a. The multimodal sensor 9a is embedded in a joint surface of the engagement protrusion 54a and the limiting groove 131a, and is configured to obtain a stress change rate and a temperature gradient in real time. The controller 7a is further configured to: determine a coupling coefficient based on the stress change rate and the temperature gradient; and in response to the coupling coefficient reaching a warning threshold, perform frequency reduction and release the air inlet pressure by adjusting the electronic proportional valve 8a.

The limiting groove 131a refers to a groove structure disposed on a peripheral side of the chamber opening 13a.

The engagement protrusion 54a refers to a protruding structure disposed on the diaphragm structure 5a and configured to mate with the limiting groove 131a, so as to achieve engagement and limiting.

The electronic proportional valve 8a refers to an electromagnetic control valve mounted at the air inlet assembly 21a outside the diaphragm pump. The electronic proportional valve 8a may continuously and proportionally adjust a cross-sectional area of an internal fluid channel thereof according to an input electrical signal (including a voltage signal or a current signal), thereby achieving a stepless adjustment of a gas flow rate or a pressure.

The multimodal sensor 9a refers to a sensing array integrated into a thin-film substrate, which simultaneously has dual sensing characteristics of temperature sensing and pressure (or strain) sensing. Through the multimodal sensor 9a, simultaneous or time-division detection of a temperature parameter and a stress parameter of a measured object may be achieved, thereby achieving cooperative monitoring of a plurality of physical quantities.

The joint surface refers to an interface region where the engagement protrusion 54a and the limiting groove 131a mutually contact and bear extrusion during a mechanical assembly process.

The stress change rate refers to a parameter configured to characterize a rate at which the stress changes over time. The stress change rate may be expressed by a first derivative of the stress of the local region of the joint surface with respect to time.

The temperature gradient refers to a parameter configured to characterize a rate at which a temperature changes over time. The temperature gradient may be expressed by a first derivative of the temperature of the local region of the joint surface with respect to time.

In some embodiments, the controller reads a pressure signal and a temperature signal output by the multimodal sensor according to a preset sampling period. For the pressure signal, the controller subtracts a pressure value at a previous moment from a pressure value at a current moment, and then divides the result by a sampling time interval, to obtain the stress change rate, thereby characterizing the rate at which the stress changes over time at the joint surface. For the temperature signal, the controller similarly subtracts a temperature value at a previous moment from a temperature value at a current moment, and then divides the result by the sampling time interval, to obtain the temperature gradient, thereby characterizing a degree of abruptness at which the temperature changes over time at the joint surface. The preset sampling period and the sampling time interval may be set based on actual needs.

The coupling coefficient refers to a value that comprehensively reflects change states of both the stress and the temperature.

In some embodiments, the controller may determine the coupling coefficient based on the stress change rate and the temperature gradient by a plurality of manners. For example, a linear coupling determination formula is pre-stored inside the controller. The formula is specifically expressed as:


C=α·Rσ+β·RT   (1)

C is the coupling coefficient (dimensionless), Rσ is the stress change rate, RT is the temperature gradient, and α and β are preset weight constants (dimensionless). It should be noted that, Rσ and RT are both subjected to normalization processing before being substituted into the formula to become dimensionless relative indicators (e.g., by division by respective reference values or maximum allowable change rates), ensuring dimensional consistency in the weighted summation. The controller substitutes the stress change rate and the temperature gradient obtained in a previous step into the above-mentioned formula, and determines a current coupling coefficient through a weighted accumulation operation. The warning threshold refers to a critical value preset to trigger a protection program.

In some embodiments, the controller compares the coupling coefficient obtained in real time with the warning threshold. When the coupling coefficient reaches or exceeds the warning threshold, the controller sends an instruction to a motor driver, and the motor driver reduces a rotation speed frequency of a motor in steps according to a preset step length. Simultaneously, the controller sends a gradually decreasing voltage signal to the electronic proportional valve. The electronic proportional valve slowly moves under a voltage drive, gradually narrowing the cross-sectional area of an air inlet channel, causing the gas flow rate to gradually decrease, thereby achieving flexible release of the air inlet pressure. The electronic proportional valve, by narrowing its own flow cross-sectional area, reduces a gas supply amount from a source, thereby causing a total gas amount and a pressure reaching an end air inlet hole to decrease accordingly.

By comprehensively evaluating a fatigue risk of the joint surface through the coupling coefficient, and by achieving a smooth reduction in a motor frequency and the flexible release of the air inlet pressure with the aid of the electronic proportional valve, direct power-off that may cause an instantaneous pressure shock inside a fluid pipeline is avoided, thereby improving the stability and safety of equipment operation.

In some embodiments, the diaphragm pump 100a further includes air path distributors 10a in communication with working chambers. The controller 7a is further configured to: determine local heat of the working chambers based on parameters of the diaphragm structure, temperature data, and the temperature gradient, through a thermal accumulation index model; and in response to the local heat of one of the working chambers reaching a heat threshold, adjust the air path distributor 10a corresponding to the working chamber, thereby reducing an intake-exhaust pressure difference of the working chamber and proportionally increasing a load of the remaining working chambers.

The working chambers refer to core regions inside the diaphragm pump configured to directly intake, compress, and discharge a conveyed medium. More descriptions regarding the working chambers may be found in the following related descriptions.

The air path distributors 10a refer to electronically controlled fluid multi-way valve assemblies configured to dynamically allocate an intake air source as needed to different working chambers or pump cover groups of the diaphragm pump 100a according to instructions of the controller.

The parameters of the diaphragm structure refer to a basic data set configured to characterize inherent physical characteristics of the diaphragm structure. The parameters of the diaphragm structure include a specific heat capacity coefficient, thermal conductivity, an effective heat reception area, or the like. The specific heat capacity coefficient refers to a physical property parameter configured to characterize a heat storage capacity of the diaphragm structure. The thermal conductivity refers to a physical property parameter configured to characterize a thermal conduction capacity of the diaphragm structure. The effective heat reception area refers to a structural dimension parameter configured to characterize the diaphragm structure that actually participates in heat exchange.

In some embodiments, the parameters of the diaphragm structure are stored in the controller in a read-only data format, and calibration and writing are completed before the device leaves the factory, and cannot be modified during operation.

The temperature data refers to local temperature values of the diaphragm structure acquired by the sensor in real time. The temperature data may be obtained through the multimodal sensor.

The local heat refers to a thermal energy evaluation value accumulated inside a single working chamber without being dissipated.

The thermal accumulation index model refers to a model configured to determine local heat of the working chamber.

In some embodiments, the thermal accumulation index model may be a machine learning model. For example, the thermal accumulation index model may be a Neural Network (NN) model, or the like, or other customized models.

In some embodiments, an input of the thermal accumulation index model includes the parameters of the diaphragm structure, the temperature data, and the temperature gradient, and an output of the thermal accumulation index model is the local heat of the working chamber.

In some embodiments, the thermal accumulation index model may be obtained in a plurality of manners. For example, the thermal accumulation index model may be obtained by training with a large number of labeled training samples, or the like.

In some embodiments, the controller may use historical parameters of the diaphragm structure, historical temperature data, and historical temperature gradient in historical data as training samples, and may use actual local heat values of each working chamber at a historical moment corresponding to the training samples as labels corresponding to the training samples. The actual local heat values refer to heat values actually measured at the historical moment.

Merely by way of example, the controller may input the training samples into an initial thermal accumulation index model, and obtain an output of the initial thermal accumulation index model. A loss function may be built based on the output and the labels corresponding to the training samples. Parameters of the initial thermal accumulation index model may be iteratively updated through a gradient descent manner, or the like, based on the loss function, until an iteration termination condition is met, and the training is completed to obtain a trained thermal accumulation index model.

The heat threshold refers to a predefined safe upper limit value of thermal energy allowed to be accumulated by a single working chamber. The heat threshold may be set based on actual needs.

The intake-exhaust pressure difference refers to a difference between exhaust pressure and intake pressure of the working chamber of the diaphragm pump.

In some embodiments, when the controller determines through comparison that the local heat of a certain working chamber exceeds the heat threshold, the controller firstly sends control instructions to a valve channel in the air path distributor corresponding to the working chamber, thereby reducing an opening degree of the valve channel and limiting an intake air volume entering the working chamber. The reduction of the intake air volume causes a compression ratio of the working chamber to decrease, with the intake-exhaust pressure difference reducing accordingly, thereby further suppressing conversion of work performed by the diaphragm structure into thermal energy. At the same time, the controller determines a cutoff flow generated by the branch due to the reduction of the opening degree. The cutoff flow refers to a difference between a target intake air volume in a normal operating state of the working chamber and an actual intake air volume after the opening degree is reduced. Subsequently, the controller superimposes the cutoff flow onto control signals of the valve channels leading to other working chambers with normal temperature, in an evenly distributed manner or according to the remaining capacity ratios of the healthy working chambers, thereby increasing the opening degrees thereof. Through the synergistic control described above, while ensuring an overall output flow of the system is constant, intelligent transfer of workload from an overheated chamber to a healthy chamber is achieved. The healthy chamber refers to a chamber among a plurality of working chambers of the diaphragm pump, whose current local heat has not exceeded the heat threshold. The remaining capacity ratio refers to a ratio of current extra load capacity receivable by a certain healthy chamber to a total receivable load capacity of all healthy chambers, configured to determine an allocation weight of the cutoff flow among each healthy chamber. The opening degree refers to an opening extent of a certain valve channel in the air path distributor.

By deriving the local heat of each working chamber in real time through the thermal accumulation index model, the system is enabled to identify early signs of overheating of a single-sided chamber in advance, and achieves forward shifting of early warning for thermal abnormality. On this basis, by dynamically adjusting, via the air path distributors and without interrupting pump operation, the intake air ratio and the intake-exhaust pressure difference of different working chambers, intelligent load balancing and adaptive allocation within the system are realized, thereby preventing forced shutdown or derating caused by overheating of any single chamber. Thus, overall efficiency of the diaphragm pump is maximized, and reliability and working efficiency of the diaphragm pump under long-term continuous operation conditions are significantly improved.

By disposing the reinforcing ribs having the heat pipe structure at the mounting boss, and connecting the reinforcing ribs to the outer casing heat sink, the thermal conduction efficiency of the working region of the diaphragm structure is effectively improved, thereby slowing down a thermal aging speed of the diaphragm structure. At the same time, in combination with a stress monitoring and feedback mechanism of the sensor and the controller, when the system detects a force overload, the system can automatically perform power-off or voltage reduction actions to protect the shell plates and the diaphragm structures from mechanical damage.

FIG. 10 is a schematic diagram illustrating a diaphragm pump according to other embodiments of the present disclosure. FIG. 11 is a schematic diagram illustrating the diaphragm pump of FIG. 10 according to some embodiments of the present disclosure. FIG. 12 is a schematic diagram illustrating the diaphragm pump of FIG. 11 from another perspective according to some embodiments of the present disclosure. FIG. 13 is a schematic diagram illustrating the diaphragm pump of FIG. 10 according to other embodiments of the present disclosure.

As shown in FIGS. 10 to 13, the present disclosure also provides a diaphragm pump 100b. It should be noted that the diaphragm pump 100b in the embodiments may be the diaphragm pump in the above-mentioned embodiments, or may be other diaphragm pumps different from those in the above-mentioned embodiments.

In some embodiments, the diaphragm pump 100b includes a pump housing 1b, an air inlet assembly 2b and an air outlet assembly 3b, a plurality of diaphragm structures, and a plurality of pump covers 4b. The pump housing 1b includes a plurality of shell plates 11b and a side plate 12b. The plurality of shell plates 11b are sequentially connected along a circumferential direction of the pump housing 1b and together with the side plate 12b enclose a pump chamber, and each of the plurality of shell plates 11b is provided with chamber openings 13b extending therethrough for communicating with the pump chamber. The air inlet assembly 2b and the air outlet assembly 3b are disposed on the side plate 12b and are spaced apart from each other. The plurality of diaphragm structures are disposed on the chamber openings in a one-to-one correspondence. A peripheral edge of each of the plurality of diaphragm structures is connected and fixed to the corresponding chamber opening 13b. The plurality of pump covers 4b are disposed to cover openings of the chamber openings 13b in a one-to-one correspondence. Each pump cover 4b, the corresponding shell plate 11b, and the corresponding diaphragm structure collectively define a working chamber, and each of the plurality of pump covers 4b is provided with an air inlet hole and an air outlet hole, the air inlet hole and the air outlet hole on the same pump cover 4b being spaced apart along a circumferential direction of the pump cover 4b. The air inlet hole and the air outlet hole of each pump cover 4b are in communication with the air inlet assembly 2b and the air outlet assembly 3b, respectively, the air inlet holes on a plurality of pump covers 4b located on the same shell plate 11b are spaced apart along an axial direction of the pump covers, and the air outlet holes on the plurality of pump covers 4b located on the same shell plate 11b are spaced apart along the axial direction of the pump covers.

By setting the internal structure of the diaphragm pump, internal fluid lines of the diaphragm pump may be arranged in a staggered manner, thereby allowing for a more reasonable and dispersed layout.

In some embodiments, each shell plate is provided with a plurality of chamber openings spaced apart along an axial direction of the shell plate; a plurality of air inlets 21b on the air inlet assembly 2b and a plurality of air outlets 31b on the air outlet assembly 3b are spaced apart along the axial direction. The plurality of air inlets 21b on the air inlet assembly 2b are spaced apart along a circumferential direction, and the plurality of air outlets 31b on the air outlet assembly 3b are spaced apart along the circumferential direction, so that the fluid lines at the side plate 12b are arranged in a staggered manner, thereby facilitating a more reasonable layout.

In some embodiments, by disposing the air inlet assembly and the air outlet assembly on the same side plate, an overall size may be reduced, and the arrangement may be more reasonable.

The diaphragm pump 100b further includes other components (e.g., a driving motor, an eccentric wheel, or the like), which will not be described in detail herein.

The diaphragm pump 100b may be a multi-faceted structure, such as a four-faceted structure or a six-faceted structure. When the diaphragm pump 100b is a four-faceted structure, a count of the corresponding shell plates 11b is four, and each shell plate 11b is provided with the chamber openings for communicating with the pump chamber. When the diaphragm pump 100b is a six-faceted structure, the count of the corresponding shell plates 11b is six, and each shell plate 11b is provided with the chamber openings for communicating with the pump chamber.

The air inlet assembly 2b and the air outlet assembly 3b are both disposed on the side plate 12b and are spaced apart from each other. Compared with a conventional approach in which at least one of the air inlet assembly 2b and the air outlet assembly 3b is mounted on the shell plate 11b adjacent to the side plate 12b, mounting both the air inlet assembly 2b and the air outlet assembly 3b on the same side plate 12b in the present disclosure can reduce a radial size. The air inlet assembly 2b and the air outlet assembly 3b are mounted on the same side plate 12b and spaced apart from each other, which can reduce the overall size and facilitate a more reasonable arrangement of the piping.

In some embodiments, the air inlet hole 491b and the air outlet hole 492b of each pump cover 4b are in communication with the air inlet assembly 2b and the air outlet assembly 3b, respectively. The air inlet holes 491b on different pump covers 4b may be connected in parallel to the air inlets 21b of the air inlet assembly 2b, or alternatively, the air inlet holes 491b on different pump covers 4b may be connected in series and then connected to the air inlets 21b of the air inlet assembly 2b.

The air inlet holes 491b on the plurality of pump covers 4b located on the same shell plate 11b are spaced apart along the axial direction, and the air outlet holes 492b on the plurality of pump covers 4b located on the same shell plate 11b are spaced apart along the axial direction.

Each shell plate 11b may be provided with a plurality of chamber openings 13b, and the plurality of chamber openings 13b on each shell plate 11b are spaced apart along the axial direction. For example, each shell plate 11b may be provided with two or three chamber openings 13b. In the present embodiment, each shell plate 11b is provided with two chamber openings 13b arranged along the axial direction. In other embodiments, a count of the chamber openings 13b on each shell plate 11b may be set according to actual needs.

The air inlet holes 491b mounted on the same shell plate 11b are connected in parallel, and the air outlet holes 492b mounted on the same shell plate 11b are connected in parallel. That is, taking the shell plate 11b including a first chamber opening and a second chamber opening as an example, correspondingly, a first pump cover 41b and a second pump cover 42b are disposed to cover the first chamber opening and the second chamber opening, respectively. Then, the air inlet hole 491b on the first pump cover 41b and the air inlet hole 491b on the second pump cover 42b may be connected in series or in parallel; similarly, the air outlet hole 492b on the first pump cover 41b and the air outlet hole 492b on the second pump cover 42b may be connected in series or in parallel, which may be specifically configured according to actual needs.

In some embodiments, the air inlet assembly 2b includes a plurality of air inlets 21b, the air outlet assembly 3b includes a plurality of air outlets 31b, and a count of the plurality of air inlets 21b, a count of the plurality of air outlets 31b, and a count of the plurality of shell plates 11b are the same. The air inlet holes 491b located on the same shell plate 11b are connected in parallel and then connected to the corresponding air inlet 21b; and the air outlet holes 492b located on the same shell plate 11b are connected in parallel and then connected to the corresponding air outlet 31b.

In a feasible embodiment, the air inlet holes 491b mounted on two adjacent shell plates 11b are connected in series or in parallel; the air outlet holes 492b mounted on the two adjacent shell plates 11b are connected in series or in parallel; or alternatively, the air inlet hole 491b and the air outlet hole 492b mounted on the same shell plate 11b are connected in series.

FIG. 12 is a schematic diagram illustrating the diaphragm pump in FIG. 11 from another perspective according to some embodiments of the present disclosure. FIG. 13 is a schematic diagram illustrating the diaphragm pump in FIG. 10 according to other embodiments of the present disclosure.

In some embodiments, as shown in FIGS. 12 and 13, among the plurality of shell plates 11b, the air inlet hole 491b and the air outlet hole 492b of the pump cover 4b on one shell plate 11b are connected in parallel or in series to form a first fluid line 5b, and all the air outlet holes 492b on the remaining shell plates 11b are connected in parallel and then connected in series with the first fluid line 5b.

Taking the diaphragm pump 100b as a four-faceted structure as an example, the diaphragm pump 100b includes a first shell plate 111b, a second shell plate 112b, a third shell plate 113b, and a fourth shell plate 114b. The first shell plate 111b includes the first pump cover 41b and the second pump cover 42b, the second shell plate 112b includes a third pump cover 43b and a fourth pump cover 44b, the third shell plate 113b includes a fifth pump cover 45b and a sixth pump cover 46b, and the fourth shell plate 114b includes a seventh pump cover 47b and an eighth pump cover 48b. In a case of a two-stage fluid line, as shown in FIG. 12, the air inlet holes 491b on the first pump cover 41b and the second pump cover 42b are connected in parallel and then connected to the air inlet assembly 2b, the air inlet holes 491b on the third pump cover 43b and the fourth pump cover 44b are connected in parallel and then connected to the air inlet assembly 2b, and the air inlet holes 491b on the fifth pump cover 45b and the sixth pump cover 46b are connected in parallel and then connected to the air inlet assembly 2b. The air outlet holes 492b of the first pump cover 41b, the second pump cover 42b, the third pump cover 43b, the fourth pump cover 44b, the fifth pump cover 45b, and the sixth pump cover 46b are all connected in parallel to form a first-stage fluid line, the air inlet holes 491b and the air outlet holes 492b of the seventh pump cover 47b and the eighth pump cover 48b are connected in parallel to form the second-stage fluid line, and the first-stage fluid line is connected in series with the second-stage fluid line.

In a case of a third-stage fluid line, as shown in FIG. 13, the air inlet holes 491b on the first pump cover 41b and the second pump cover 42b are connected in parallel and then connected to the air inlet assembly 2b, the air inlet holes 491b on the third pump cover 43b and the fourth pump cover 44b are connected in parallel and then connected to the air inlet assembly 2b, and the air inlet holes 491b on the fifth pump cover 45b and the sixth pump cover 46b are connected in parallel and then connected to the air inlet assembly 2b; the air outlet hole 492b of the first pump cover 41b, the air outlet hole 492b on the second pump cover 42b, the air outlet hole 492b on the third pump cover 43b, the air outlet hole 492b on the fourth pump cover 44b, the air outlet hole 492b on the fifth pump cover 45b, and the air outlet hole 492b on the sixth pump cover 46b are all connected in parallel to form a first-stage fluid line, the air inlet hole 491b of the seventh pump cover 47b and the air outlet hole 492b of the seventh pump cover 47b are connected in series to form a second-stage fluid line, the air inlet hole 491b of the eighth pump cover 48b and the air outlet hole 492b of the eighth pump cover 48b are connected in series to form a third-stage fluid line, and the first-stage fluid line, the second-stage fluid line, and the third-stage fluid line are connected in series to form a three-stage fluid line.

FIG. 14 is a schematic diagram illustrating the pump cover according to some embodiments of the present disclosure.

In some embodiments, as shown in FIGS. 10-14, the diaphragm pump 100b further includes an electromagnetic proportional needle valve 6b and a controller 7b. The diaphragm structure includes an engagement protrusion (i.e., the aforesaid engagement protrusion 54a). The remaining shell plates are end-stage shell plates, and a back pressure compensation annular chamber 411b and a flexible pressing ring 412b embedded in the back pressure compensation annular chamber 411b are provided inside the pump cover 4b located on the end-stage shell plate. An open side of the flexible pressing ring 412b faces an interior of the back pressure compensation annular chamber 411b. The pump cover 4b is provided with a pressure-introducing inclined hole 413b for communicating a final-stage working chamber with the back pressure compensation annular chamber 411b. The electromagnetic proportional needle valve 6b is disposed at the pressure-introducing inclined hole 413b and is controlled by the controller 7b. The controller 7b is configured to: obtain a temperature gradient; and in response to the temperature gradient reaching a temperature threshold, control the electromagnetic proportional needle valve to release fluid within the back pressure compensation annular chamber, so as to reduce a downward pressing force of the flexible pressing ring.

The electromagnetic proportional needle valve 6b refers to a miniaturized electromagnetic control valve that utilizes electromagnetic force to drive a valve needle to generate a controllable displacement, thereby adjusting an opening degree of a fluid channel.

The end-stage shell plate refers to a shell plate located at a most downstream end of an airflow path in a multi-stage fluid line structure and configured to bear maximum final output air pressure.

The back pressure compensation annular chamber 411b refers to an annular hollow channel formed by machining on an inner wall of the pump cover 4b corresponding to the end-stage shell plate.

The flexible pressing ring 412b refers to an annular sealing auxiliary component with an elastic expansion deformation capability, mounted within the back pressure compensation annular chamber 411b. In some embodiments, a cross-section of the flexible pressing ring 412b may be U-shaped, or the like. The open side of the flexible pressing ring 412b refers to a U-shaped opening end of the flexible pressing ring 412b, facing an interior of the back pressure compensation annular chamber 411b.

The pressure-introducing inclined hole 413b refers to a bypass air path channel extending through an interior of the pump cover 4b and communicating the final-stage working chamber with the back pressure compensation annular chamber 411b.

The final-stage working chamber refers to a high-pressure fluid working space formed between the end-stage shell plate and the diaphragm structure.

More descriptions regarding a manner for obtaining the temperature gradient may be found elsewhere in the present disclosure (e.g., FIGS. 5-7 and related descriptions thereof).

The temperature threshold refers to a preset critical value of a temperature change rate representing a risk of device overheating.

The downward pressing force refers to a mechanical pressing force applied vertically to the engagement protrusion by the flexible pressing ring 412b after the flexible pressing ring 412b expands in response to receiving internally introduced gas pressure.

In some embodiments, after fluid enters the back pressure compensation annular chamber 411b via the pressure-introducing inclined hole 413b, it flows into an interior of an opening of the flexible pressing ring 412b. The fluid pressure causes the flexible pressing ring 412b to expand downward, thereby generating the downward pressing force and causing the engagement protrusion to be pressed tightly.

In some embodiments, the controller compares the obtained temperature gradient with the temperature threshold. When the temperature gradient exceeds the temperature threshold, the controller outputs a control current to the electromagnetic proportional needle valve, whereupon the valve needle inside the electromagnetic proportional needle valve immediately retracts, opening a pressure relief channel. At this time, a portion of high-pressure fluid within the back pressure compensation annular chamber is discharged via the needle valve, and the gas pressure within the flexible pressing ring decreases accordingly. The flexible pressing ring retracts upward based on its inherent elasticity, and the downward pressing force it applies to the engagement protrusion below is correspondingly weakened.

In some embodiments, the diaphragm pump further includes a thermistor 9b embedded in a bottom of the engagement protrusion, and an acoustic emission sensor 10b disposed outside the pump cover 4b. The controller 7b is connected to the thermistor 9b and the acoustic emission sensor 10b, respectively. The controller 7b is further configured to: in response to the temperature gradient detected by the thermistor 9b reaching the temperature threshold, control the electromagnetic proportional needle valve to reduce the pressure in the back pressure compensation annular chamber by a preset step value; and in response to the acoustic emission sensor 10b capturing a preset acoustic frequency band, control the electromagnetic proportional needle valve to be reversely closed and locked at a preset closing amount.

The thermistor 9b refers to a semiconductor temperature-sensing element whose resistance value varies with an absolute change in temperature.

The acoustic emission sensor 10b refers to a sensing device for detecting minute vibrations (displacements) generated on a surface of an object due to deformation or damage of a material of the object, and converting the minute vibrations (displacements) into electrical signals. In some embodiments, the acoustic emission sensor 10b may be a high-frequency acoustic emission sensor, and its operating frequency band covers a high-frequency range (e.g., 100 kHz to 1 MHz).

In some embodiments, when manufacturing the diaphragm structure, the thermistor 9b is encapsulated within an innermost bottom end of the engagement protrusion. The high-frequency acoustic emission sensor 10b is fixedly mounted on a metal housing outside the pump cover 4b. Signal lines of the thermistor 9b and the acoustic emission sensor 10b are connected to input interfaces of the controller 7b, respectively. A voltage signal output by the thermistor 9b is configured to characterize temperature; and a voltage waveform output by the acoustic emission sensor 10b is configured to reflect vibration and sound information.

More descriptions regarding a manner for determining the temperature gradient may be found elsewhere in the present disclosure (e.g., FIGS. 5-7 and related descriptions thereof).

The preset step value refers to a fixed increment of a single output change set by the controller. The preset step value may be set based on actual needs.

In some embodiments, when the temperature gradient determined by the controller based on the thermistor reaches the temperature threshold, the controller initiates a depressurization procedure and outputs a progressively increasing control level signal to the electromagnetic proportional needle valve. An increment of each control level signal is fixed to the preset step value. A valve port of the needle valve is gradually opened at a minute step size corresponding to the preset step value, causing the fluid within the back pressure compensation annular chamber to be slowly discharged. During the process, the gas pressure within the back pressure compensation annular chamber gradually decreases in a stepped manner.

The preset acoustic frequency band refers to a set specific sound frequency range representing sound generated when fluid leaks from a gap. The preset closing amount refers to a determined stroke control command value set by the controller for driving the electromagnetic proportional needle valve to move reversely and reduce a pressure relief cross-sectional area.

The preset acoustic frequency band and the preset closing amount may be set based on actual needs.

In some embodiments, during a process of slow depressurization, a pressing force applied by the flexible pressing ring to the engagement protrusion gradually decreases. When the pressing force drops to a level just unable to maintain sealing, a small amount of high-pressure gas is ejected from a gap of the engagement protrusion, inducing a high-frequency whistling sound. The acoustic emission sensor captures a vibration waveform of an outer casing, and the controller processes the waveform signal through frequency domain transformation. Once the controller determines that a signal frequency falls within the preset acoustic frequency band, it is determined that the diaphragm pump has reached a leakage critical point. The controller immediately terminates the depressurization procedure, and decreases the control level of the electromagnetic proportional needle valve by the preset closing amount. The valve needle of the electromagnetic proportional needle valve retracts, causing a pressure relief area of the valve port to slightly close, whereby the pressure within the back pressure compensation annular chamber slightly increases, thereby pressing the engagement protrusion tightly again and eliminating leakage. Thereafter, the controller locks a level signal of the electromagnetic proportional needle valve to the fixed value and maintains it constant.

By combining the thermistor at the bottom and the acoustic emission sensor outside, high-precision dynamic optimal control can be achieved. The control manner performs stepwise minute pressure relief, and completes a re-locking action at the moment when a weak leakage sound is detected. During the entire operating cycle, an optimal mechanical balance point that maintains sealing without leakage while minimizing an edge friction pressing force can be automatically determined.

High-pressure fluid enters the interior of the flexible pressing ring via the pressure-introducing inclined hole 413b, and automatically enhances a pressing action on the diaphragm structure based on own pressure of the high-pressure fluid. By monitoring the temperature gradient in real time, when it is detected that frictional heat generation exceeds the temperature threshold, the electromagnetic proportional needle valve is controlled to actively open for pressure relief, so that the flexible pressing ring appropriately retracts, thereby preventing the diaphragm structure from being damaged due to cracking caused by excessive compression under high pressure and high temperature conditions.

FIG. 15 is a schematic structural diagram illustrating a diaphragm pump according to yet other embodiments of the present disclosure. FIG. 16 is a schematic cross-sectional structural diagram illustrating the diaphragm pump of FIG. 15 according to some embodiments of the present disclosure. FIG. 17 is a schematic enlarged cross-sectional structural diagram illustrating a diaphragm sheet and a pump cover of FIG. 15 according to some embodiments of the present disclosure. FIG. 18 is a schematic cross-sectional structural diagram illustrating the diaphragm pump of FIG. 15 according to other embodiments of the present disclosure. FIG. 19 is a schematic structural diagram illustrating an eccentric member of FIG. 15 according to some embodiments of the present disclosure.

As shown in FIGS. 15 to 19, the present disclosure provides a diaphragm pump 1000c. It should be noted that, the diaphragm pump 1000c in the present embodiment may be the diaphragm pump in the above-described embodiments or other diaphragm pumps different from those in the above-described embodiments. Similarly, one or more embodiments in the present embodiment may be combined with one or more embodiments in the above-described embodiments, and should also have the effects possessed by the above-described embodiments, which will not be described in detail herein.

In some embodiments, as shown in FIGS. 15 to 16, a pump chamber structure 100c for the diaphragm pump includes a chamber body 1c, a plurality of pump covers 2c, a pump shaft 3c, and a plurality of transmission components 4c. The chamber body 1c is hollow and has a plurality of peripheral sidewalls sequentially connected along a circumferential direction of the chamber body 1c. Each of the plurality of peripheral sidewalls is provided with chamber openings 11c, and the chamber openings 11c on the two peripheral sidewalls disposed opposite to each other are disposed opposite to each other. The plurality of pump covers 2c are disposed to cover the plurality of chamber openings 11c in a one-to-one correspondence. The pump shaft 3 at least partially extends through the chamber body 1c. The plurality of transmission components 4c are sequentially disposed within the chamber body 1c along an axial direction of the pump shaft 3. One end of each of the plurality of transmission components 4c is rotatably connected to the pump shaft 3, and the other end of each of the plurality of transmission components 4c is disposed to cover the corresponding chamber opening 11c and collectively defines a working chamber together with the corresponding pump cover 2c. The plurality of transmission components 4c are structurally identical.

The pump chamber structure 100c refers to a mechanical assembly for fluid delivery or pressurization. It is composed of the chamber body 1c, the pump cover 2c, the pump shaft 3c, and the transmission component 4c, and a number of working chambers are formed therein to realize suction and discharge of fluid.

The pump shaft 3c refers to a power input or transmission shaft, which at least partially extends into the chamber body 1c and is configured to drive the plurality of transmission components 4c to perform reciprocating or rotational movement.

The transmission components 4c refer to motion conversion units mounted inside the pump chamber structure 100c, and are configured to convert the rotational movement of the pump shaft 3c into reciprocating deformation of the diaphragm sheets, thereby changing volumes of the working chambers and realizing suction and discharge of fluid.

In the present embodiment, the pump covers 2c are disposed to cover the plurality of chamber openings 11c of the chamber body 1c in a one-to-one correspondence, and cooperate with the plurality of transmission components 4c in a one-to-one correspondence to form a plurality of working chambers, thereby forming a plurality of power sources for gas or liquid delivery. The plurality of transmission components 4c are all accommodated in the chamber body 1c, and the plurality of transmission components 4c are sequentially arranged within the chamber body 1c along the axial direction of the pump shaft 3. One end of each transmission component 4c is rotatably connected to the pump shaft 3, and the other end is disposed to cover the corresponding chamber opening 11c. The configuration allows the plurality of transmission components 4c to be driven to move under the rotational action of the same pump shaft 3. The movement of each transmission component 4c thereby causes gas or liquid to flow in the working chamber, so as to provide power for the gas or liquid to flow in a delivery pipeline. The plurality of transmission components 4c are structurally identical. The chamber openings 11c on the two peripheral sidewalls of the chamber body 1c that are disposed opposite to each other are disposed opposite to each other, thereby allowing the transmission components 4c to also be symmetrically disposed on both sides of the pump shaft 3. Therefore, when the diaphragm pump 1000c operates, the plurality of transmission components 4c are arranged in a balanced manner, which makes operation more stable, generates less vibration and noise, and results in higher working efficiency. Furthermore, the plurality of transmission components 4c are arranged side by side, resulting in a more compact structure, thereby causing the entire diaphragm pump 1000c to have a smaller volume.

In some embodiments, to better allow suction power to be formed in the working chambers, each transmission component 4c has a stroke along the radial direction of the pump shaft 3. Through the movement of each transmission component 4c, the volume of each working chamber changes, thereby forming the suction power.

In some embodiments, each transmission component 4c is eccentrically connected to the pump shaft 3. The rotation of the pump shaft 3 drives each transmission component 4c to generate a stroke along the radial direction of the pump shaft 3, thereby forming the suction power. Moreover, the plurality of transmission components 4c are structurally consistent and are all connected to the pump shaft 3. Therefore, the plurality of transmission components 4c have better working consistency. When the diaphragm pump 1000c operates, the whole will not be offset, resulting in better stability and more stable operation of the diaphragm pump 1000c.

The chamber body 1c has a polygonal configuration so as to have a plurality of peripheral sidewalls. In some embodiments, as shown in FIG. 15, a count of the peripheral sidewalls is an even number greater than or equal to 4. For example, the chamber body 1c may be a tetrahedron, a hexahedron, octahedron, or the like, thereby causing every two peripheral sidewalls to be disposed opposite to each other. Therefore, a count of the transmission components 4c is also a corresponding even number, which may be more uniformly and symmetrically arranged along the circumferential direction of the pump shaft 3. During operation, the acting forces of the two symmetrically disposed transmission components 4c on the pump shaft 3 may cancel each other out, thereby causing the pump shaft 3 to be more balanced during operation and thus more stable.

In some embodiments, with reference to FIGS. 16 and 18, each transmission component 4c includes an eccentric member 41c, a bearing 42c, a transmission rod 43c, and a diaphragm sheet 44c. The eccentric member 41c is fixedly sleeved on an outer side of the pump shaft 3. The bearing 42c is sleeved on an outer side of the eccentric member 41c. One end of the transmission rod 43c is sleeved on an outer peripheral side of the bearing 42c. The diaphragm sheet 44c is connected to the other end of the transmission rod 43c and is disposed to cover the corresponding chamber opening 11c. The bearings 42c of the plurality of transmission components 4c are arranged side by side along the axial direction of the pump shaft 3. The two eccentric members 41c of the two transmission components 4c covering the two chamber openings 11c disposed opposite to each other are formed integrally as a single piece. The transmission rod 43c is threadedly connected to the corresponding diaphragm sheet 44c.

The rotation of the pump shaft 3 may drive the eccentric member 41c to rotate together. Under the pushing action of the eccentric member 41c, the bearing 42c is driven to generate a displacement along the radial direction of the pump shaft 3, thereby causing the transmission rod 43c to move along the radial direction of the pump shaft 3, and thereby driving the diaphragm sheet 44c to move along the radial direction of the pump shaft 3, so as to change the volume of the working chamber. Each diaphragm sheet 44c is integrally formed, and at least portions thereof forming the working chamber have elastic deformability. Through the movement of the transmission rod 43c, the transmission rod 43c presses against the diaphragm sheet 44c, so that the diaphragm sheet 44c undergoes elastic deformation to act on an external delivery pipe by suction, thereby providing air flow power.

The eccentric member 41c refers to an eccentric sleeve type component configured to synchronously rotate with the pump shaft 3c, generate an eccentric motion trajectory, and drive the bearing and subsequent components to perform periodic oscillation.

The outer side of the eccentric member 41c refers to an outer cylindrical surface of the eccentric member 41c and a radial outer space occupied thereby.

In some embodiments, the two eccentric members 41c of the two transmission components 4c disposed to cover the two chamber openings 11c that are disposed opposite to each other are formed integrally as a single piece. Taking the chamber body 1c as a tetrahedron as an example, the chamber body 1c has two peripheral sidewalls disposed opposite to each other along an up-down direction, and two peripheral sidewalls disposed opposite to each other along a left-right direction. At this time, four transmission components 4c are also provided and evenly spaced apart along the circumferential direction of the pump shaft 3. Among the two transmission components 4c connected to the two chamber openings 11c disposed opposite to each other along the up-down direction, the two eccentric members 41c are formed integrally as a single piece. In the two transmission components 4c connected to the two chamber openings 11c disposed opposite to each other along the left-right direction, the two eccentric members 41c are formed integrally as a single piece. Furthermore, the eccentric directions of the two integrally formed eccentric members 41c are symmetrically disposed along the radial direction of the pump shaft 3, thereby causing displacements of the two transmission components 4c along the radial direction to be more consistent and symmetrical during operation, and thus allowing acting forces on the pump shaft 3 to be more balanced. The eccentric direction of the eccentric member 41c refers to a direction of deviation of a geometric center of an outer circle of the eccentric member 41c relative to a rotational axis of the pump shaft 3c.

In some embodiments, with reference to FIGS. 16 and 18, the eccentric member 41c includes a connecting post 411c. An eccentric hole 412c is eccentrically provided on the connecting post 411c, and the eccentric hole 412c is sleeved on an outer peripheral side of the pump shaft 3. The bearing 42c is sleeved on an outer peripheral side of the corresponding connecting post 411c.

The connecting post 411c has a cylindrical configuration. The eccentric hole 412c extends therethrough along the axial direction of the pump shaft 3, and the eccentric hole 412c is sleeved on the outer peripheral side of the pump shaft 3. The bearing 42c allows one end of the transmission rod 43c to be sleeved on an outer side of the connecting post 411c. Therefore, when the pump shaft 3 rotates, the pump shaft 3 may drive the connecting post 411c to rotate together, thereby causing the bearing 42c to generate a displacement along the radial direction of the pump shaft 3 under the action of eccentric force, and thus causing the transmission rod 43c and the diaphragm sheet 44c to generate a displacement along the radial direction of the pump shaft 3.

The outer peripheral side of the connecting post 411c refers to the outer cylindrical surface of the cylinder of the connecting post 411c and the radial outer space occupied thereby.

The bearing 42c refers to a rolling or sliding bearing sleeved on an outer side of the eccentric member 41c.

The outer peripheral side of the bearing 42c refers to the outer cylindrical surface of the outer ring of the bearing 42c and the radial outer space occupied thereby.

In some embodiments, each transmission rod 43c is threadedly connected to the corresponding diaphragm sheet 44c. Each diaphragm sheet 44c has a connecting end and a closed end disposed opposite to each other along a radial direction of the pump shaft 3. The connecting end is threadedly connected to the transmission rod 43c, to facilitate the assembly and disassembly of the diaphragm sheet 44c and the transmission rod 43c. The shape of the closed end matches the shape of the chamber opening 11c, thereby better closing the corresponding chamber opening 11c. The diaphragm sheet 44c further includes a transition section connected between the connecting end and the closed end. Along a radially outward direction of the pump shaft 3, a diameter of the transition section gradually increases. In some embodiments, the connecting end, the closed end, and the transition section are integrally formed, which provides better strength and is easier to manufacture.

In some embodiments, with reference to FIGS. 16 and 17, when the chamber opening 11c has a circular configuration, the closed end is in a disk shape adapted to the chamber opening 11c.

In some embodiments, a groove 12c is provided around a periphery of the chamber opening 11c, an engagement protrusion 441c is provided on the diaphragm sheet 44c, the engagement protrusion 441c is engaged in the corresponding groove 12c, and the pump cover 2c is press-connected to an outer side of the diaphragm sheet 44c.

In some embodiments, the engagement protrusion 441c is annularly provided at the edge of the closed end and protrudes from a side of the closed end facing the pump shaft 3. A peripheral edge of the closed end of the diaphragm sheet 44c is engaged in the chamber body 1c, thereby limiting the diaphragm sheet 44c to a corresponding peripheral side surface of the chamber body 1c. When the diaphragm sheet 44c cannot move relative to the peripheral side surface of the chamber body 1c, the entire transmission component 4c will not move relative to the axial direction and the circumferential direction of the chamber body 1c and the pump shaft 3, which may better ensure the relative positions between the plurality of transmission components 4c.

At least a portion of the pump cover 2c may extend into the chamber opening 11c and be press-connected to the diaphragm sheet 44c, so as to press the engagement protrusion 441c into the corresponding groove 12c. The pump cover 2c is press-connected to the corresponding diaphragm sheet 44c, thereby causing the diaphragm sheet 44c not to detach from the chamber opening 11c. An air inlet hole and an air outlet hole are provided on the pump cover 2c. An air inlet pipe fitting is correspondingly connected at the air inlet hole, and an air outlet pipe fitting is correspondingly connected at the air outlet hole. Through the pulsation of the diaphragm sheet 44c, airflow may enter the working chamber from the air inlet hole and then flow out from the air outlet hole.

According to different design requirements, the counts of the corresponding chamber openings 11c and the transmission components 4c also vary.

In some embodiments, a plurality of chamber openings 11c arranged along a same arc in the circumferential direction of the chamber body 1c constitute a group of chamber openings 11c. A plurality of transmission components 4c correspondingly arranged with the same group of chamber openings 11c constitute a group of transmission components 4c. The plurality of transmission rods 43c in the same group of transmission components 4c are spaced apart along the circumferential direction of the pump shaft 3, and the plurality of transmission rods 43c in the same group of transmission components 4c are structurally identical and are each bent.

Taking the chamber body 1c as a tetrahedron as an example, the bearings 42c of the four transmission components 4c are sequentially arranged side by side along the axial direction of the pump shaft 3. Therefore, each bearing 42c is not centrally aligned with the corresponding chamber opening 11c along the radial direction. The plurality of transmission rods 43c in a group of transmission components 4c are consistent and are each bent, which may better ensure the stability of the diaphragm pump 1000c during operation, and also makes the structure simpler and assembly easier.

In some embodiments, with reference to FIGS. 15 and 16, the chamber openings 11c may be provided with two groups, and the two groups of chamber openings 11c are spaced apart along the axial direction of the pump shaft 3. Correspondingly, the transmission components 4c are also provided with two groups. The two groups of transmission components 4c are arranged in a one-to-one correspondence with the two groups of chamber openings 11c, and the two groups of transmission components 4c are completely identical, which is easier to manufacture and more conducive to ensuring the smoothness of the diaphragm pump 1000c during operation.

The present disclosure also provides a diaphragm pump 1000c. The diaphragm pump 1000c includes the above-described pump chamber structure 100c. The pump chamber structure 100c makes the overall structure of the diaphragm pump 1000c more compact, smaller in volume, and lower in cost, and also makes it more stable during operation, less prone to shaking and displacement, and more efficient.

FIG. 20 is a schematic structural diagram illustrating a pump chamber structure according to some embodiments of the present disclosure. FIG. 21 is an exploded schematic structural diagram illustrating the pump chamber structure of FIG. 20 according to some embodiments of the present disclosure. FIG. 22 is a sectional schematic structural diagram illustrating the pump chamber structure of FIG. 20 according to some embodiments of the present disclosure. FIG. 23 is an enlarged schematic structural diagram illustrating detail A of FIG. 22 according to some embodiments of the present disclosure. FIG. 24 is a schematic structural diagram illustrating a diaphragm pump according to still other embodiments of the present disclosure.

As shown in FIG. 20 to FIG. 24, the present disclosure provides a pump chamber structure 100d and a diaphragm pump 1000d. It should be noted that the diaphragm pump 1000d in the present embodiment may be the diaphragm pump in the above-mentioned embodiments, or may be other diaphragm pumps different from those in the above-mentioned embodiments. Similarly, one or more embodiments in the present embodiment may be combined with one or more embodiments in the above-mentioned embodiments, and it should also have the effects possessed by the above-mentioned embodiments, without further elaboration.

In some embodiments, as shown in FIG. 20 to FIG. 21, the pump chamber structure 100d includes a chamber housing 1d, a pump shaft 2d, and a plurality of sets of connecting rod assemblies 3d. The chamber housing 1d has a plurality of peripheral side surfaces, each of the plurality of peripheral side surfaces is provided with at least one chamber opening 11d. The pump shaft 2d is disposed within the chamber housing 1d along an axial direction of the chamber housing 1d. The plurality of sets of connecting rod assemblies 3d are arranged side by side within the chamber housing 1d along an axial direction of the pump shaft 2d. One end of each set of the plurality of sets of connecting rod assemblies 3d is sleeved on an outer peripheral side of the pump shaft 2d, and the other end of each set of the plurality of sets of connecting rod assemblies 3d extends into the corresponding chamber opening 11d. The chamber housing 1d is provided with a plurality of limiting portions, an end of each set of the plurality of sets of connecting rod assemblies 3d extending into the chamber opening 11d is provided with a mating portion, and the limiting portion cooperates with the corresponding mating portion to limit movement of the corresponding connecting rod assembly 3d along the axial direction of the pump shaft 2d.

In the present embodiment, the chamber housing 1d is provided with the plurality of peripheral side surfaces. The plurality of peripheral side surfaces may be an even number of peripheral side surfaces greater than or equal to four. For example, the chamber housing 1d may be configured as a tetrahedron, a hexahedron, or the like. At least one chamber opening 11d may be provided on each peripheral side surface, and the plurality of sets of connecting rod assemblies 3d are configured to correspond to the plurality of chamber openings 11d to form a plurality of working chambers, thereby improving the working efficiency of the diaphragm pump 1000d.

The chamber housing 1d is provided with the plurality of limiting portions, and an end of each set of the plurality of sets of connecting rod assemblies 3d extending into the chamber opening 11d is provided with the mating portion. The limiting portion cooperates with the corresponding mating portion to limit movement of the corresponding connecting rod assembly 3d along the axial direction of the pump shaft 2d, such that each set of the connecting rod assemblies 3d is restrained in position relative to the pump shaft 2d and the chamber opening 11d, thereby making each working chamber more stable during operation and less prone to leakage. Furthermore, the position of the connecting rod assembly 3d relative to the pump shaft 2d is also more stable, the relative positions among the plurality of sets of connecting rod assemblies 3d are more stable during operation and are less prone to mutual extrusion, thereby better ensuring the working stability of the entire diaphragm pump 1000d.

The limiting portion refers to a protrusion, a step, or a groove structure disposed on the chamber housing.

The mating portion refers to a structure disposed at an end of the connecting rod assembly extending into the chamber opening (e.g., a flange, a claw, a collar, a recess, or the like).

For convenience of description below, a specific structure of the pump chamber structure 100d will be described by taking the chamber housing 1d having four peripheral side surfaces as an example. Other polyhedral chamber housings 1d may be implemented adaptively with reference thereto.

In some embodiments, as shown in conjunction with FIG. 22 and FIG. 23, each of the plurality of limiting portions includes a limiting groove 12d disposed on a peripheral side of the chamber opening 11d, the mating portion includes an engagement protrusion 321d disposed at an end of the connecting rod assembly 3d, and the engagement protrusion 321d is in an engaged connection with the corresponding limiting groove 12d to limit movement of the connecting rod assembly 3d along the axial direction and the circumferential direction of the pump shaft 2d.

The peripheral side of the chamber opening 11d refers to a surface region of the chamber housing around an outer side of an opening edge of the chamber opening 11d.

The end of the connecting rod assembly 3d refers to an end region of the connecting rod assembly 3d along its longitudinal direction, that is, a side extending into the interior of the chamber opening 11d.

By the engagement protrusion 321d being engaged in the corresponding limiting groove 12d, the connecting rod assembly 3d is thereby prevented from being displaced on the corresponding peripheral side surface of the chamber housing 1d, thus preventing the connecting rod assembly 3d from moving relative to the pump shaft 2d.

It may be understood that, for chamber openings 11d of different shapes and sizes, the corresponding limiting grooves 12d may also have different shapes and sizes, and thus the engagement protrusions 321d may also have different shapes and sizes. In some embodiments, the shape of the engagement protrusion 321d matches the shape of the limiting groove 12d, such that the engagement protrusion 321d can be better engaged in the corresponding limiting groove 12d, thereby providing a better engagement fit and thus a better limiting effect.

In some embodiments, the limiting groove 12d is a full-circumference annular groove disposed around the peripheral side of the corresponding chamber opening 11d, and the engagement protrusion 321d is a full-circumference annular protrusion. With the full-circumference annular protrusion 321d engaged in the full-circumference annular groove 12d, limiting is achieved in all directions along a plane where the peripheral side surface of the chamber housing 1d is located, thus providing a better limiting effect. The shape of the engagement protrusion 321d and the shape of the corresponding limiting groove 12d may not be completely identical. For example, the engagement protrusion 321d includes a plurality of protruding portions spaced apart along a circumferential direction of the chamber opening 11d, the plurality of protruding portions are uniformly distributed at intervals along a circumferential direction of the limiting groove 12d, and may also limit relative positions of the connecting rod assembly 3d and the chamber housing 1d in a plurality of directions.

In some embodiments, the limiting groove 12d includes a plurality of groove sections spaced apart along the circumferential direction of the chamber opening 11d, the engagement protrusion 321d includes the plurality of protruding portions spaced apart along the circumferential direction of the chamber opening 11d, the plurality of protruding portions are engaged in the plurality of groove sections in a one-to-one correspondence; or, the engagement protrusion 321d is the full-circumference annular protrusion. By engaging the full-circumference annular protrusion 321d by the plurality of groove sections, or by engaging the plurality of groove sections with the plurality of protruding portions in a one-to-one correspondence, relative positions of the connecting rod assembly 3d and the chamber housing 1d is limited, thereby ensuring proper positioning of the connecting rod assembly 3d relative to the pump shaft 2d.

In some embodiments, as shown in conjunction with FIG. 21 and FIG. 22, each set of the plurality of sets of connecting rod assemblies 3d includes a connecting rod 31d and a diaphragm sheet 32d. One end of the connecting rod 31d is rotatably sleeved on an outer side of the pump shaft 2d; one end of the diaphragm sheet 32d is connected to the other end of the connecting rod 31d, and the other end of the diaphragm sheet 32d extends into the corresponding chamber opening 11d. The engagement protrusion 321d is provided on the other end of the diaphragm sheet 32d and is received in the limiting groove 12d, so that the diaphragm sheet 32d closes the chamber opening 11d.

By the diaphragm sheet 32d being connected to the chamber housing 1d and by the connecting rod 31d being connected to the pump shaft 2d, the positions of the connecting rod 31d and the diaphragm sheet 32d are completely limited.

In some embodiments, the diaphragm sheet 32d has a connecting end and a closed end disposed opposite to each other along a radial direction of the pump shaft 2d, the connecting end is in threaded connection with the connecting rod 31d so as to facilitate disassembly and assembly of the diaphragm sheet 32d and the connecting rod 31d, and a shape of the closed end matches a shape of the chamber opening 11d, thereby better closing the corresponding chamber opening 11d. The diaphragm sheet 32d further includes a transition section connected between the connecting end and the closed end, and along a radially outward direction of the pump shaft 2d, a diameter of the transition section gradually increases. In some embodiments, the connecting end, the closed end, and the transition section are integrally disposed, resulting in better strength and more convenient manufacturing.

In some embodiments, the chamber opening 11d is circular, and the closed end is in a disk shape adapted to the chamber opening 11d. The engagement protrusion 321d is annularly provided at an edge of the closed end and protrudes from a side of the closed end facing the pump shaft 2d.

The closed end of the diaphragm sheet 32d is retained on the chamber housing 1d by the peripheral edge thereof engaging with the corresponding peripheral side surface of the chamber housing 1d, such that the diaphragm sheet 32d is restricted from moving relative to the peripheral side surface. When the diaphragm sheet 32d is restrained from moving relative to the peripheral side surface, the entire connecting rod assembly 3d is prevented from moving relative to the chamber housing 1d and the pump shaft 2d, thereby better ensuring the relative positions of the plurality of sets of connecting rod assemblies 3d.

In some embodiments, as shown in conjunction with FIG. 20 to FIG. 22, the pump chamber structure 100d further includes a plurality of pump covers 4d connected to the chamber housing 1d, the plurality of pump covers 4d are disposed to cover the plurality of chamber openings 11d in a one-to-one correspondence, and at least a portion of each of the plurality of pump covers 4d is capable of extending into the chamber opening 11d and being press-connected to the diaphragm sheet 32d, so as to press-connect the engagement protrusion 321d in the corresponding limiting groove 12d.

By the pump cover 4d being press-connected to the corresponding diaphragm sheet 32d, the diaphragm sheet 32d is prevented from detaching from the chamber opening 11d. Furthermore, a working chamber is formed between the pump cover 4d and the corresponding diaphragm sheet 32d.

Each connecting rod 31d is eccentrically connected to the pump shaft 2d. When the pump shaft 2d rotates under the drive of a drive motor 200d, the connecting rod 31d forms an active stroke in the radial direction along the pump shaft 2d under the rotation of the pump shaft 2d. Furthermore, the diaphragm sheet 32d is elastically disposed, and the movement of the connecting rod 31d drives the diaphragm sheet 32d to undergo elastic deformation and movement, thereby forming a pulsating force to cause gas or liquid to flow.

The eccentric connection refers to an assembly relationship between the connecting rod and the pump shaft, with a connecting point of the connecting rod having a fixed radial offset with respect to a rotation axis of the pump shaft. When the pump shaft rotates, the eccentric connection causes the connecting rod to generate radial reciprocating motion, thereby driving the diaphragm sheet to achieve a pumping function.

The present disclosure also provides the diaphragm pump 1000d. As shown in FIG. 24, the diaphragm pump 1000d includes the pump chamber structure 100d described above, the drive motor 200d, and a fan 300d. The drive motor 200d is operable to drive the pump shaft 2d of the pump chamber structure 100d to rotate, and the fan 300d is operable to dissipate heat from the drive motor 200d. The drive motor 200d, the fan 300d, and the pump shaft 2d are all coaxially disposed, resulting in a more compact structure and a smaller volume.

Each technical feature of the above-mentioned embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the respective technical features of the above-mentioned embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should all be considered within the scope of the present disclosure.

Apparently, the embodiments described above are merely some embodiments of the present disclosure, and not all embodiments. Based on the embodiments in the present disclosure, those of ordinary skill in the art may make other changes or variations in different forms without inventive effort, all of which should fall within the scope of protection of the present disclosure.

Claims

1. A diaphragm pump, comprising:

a pump housing, including a plurality of shell plates and a side plate, wherein the plurality of shell plates are sequentially connected along a circumferential direction of the pump housing and together with the side plate enclose a pump chamber, and each of the plurality of shell plates is provided with chamber openings extending therethrough for communicating with the pump chamber;
an air inlet assembly and an air outlet assembly, disposed on the side plate and spaced apart from each other;
a plurality of diaphragm structures, disposed on the chamber openings in a one-to-one correspondence, wherein a peripheral edge of each of the plurality of diaphragm structures is connected and fixed to the corresponding chamber opening;
a plurality of pump covers, disposed to cover openings of the chamber openings in a one-to-one correspondence, wherein each pump cover, the corresponding shell plate, and the corresponding diaphragm structure collectively define a working chamber, and each of the plurality of pump covers is provided with an air inlet hole and an air outlet hole, the air inlet hole and the air outlet hole on the same pump cover being spaced apart along a circumferential direction of the pump cover;
wherein the air inlet hole and the air outlet hole of each pump cover are in communication with the air inlet assembly and the air outlet assembly, respectively, the air inlet holes on a plurality of pump covers located on the same shell plate are spaced apart along an axial direction of the pump covers, and the air outlet holes on the plurality of pump covers located on the same shell plate are spaced apart along the axial direction of the pump covers.

2. The diaphragm pump of claim 1, wherein each shell plate is provided with a plurality of chamber openings spaced apart along an axial direction of the shell plate; a plurality of air inlets on the air inlet assembly and a plurality of air outlets on the air outlet assembly are spaced apart along the axial direction; and the plurality of air inlets on the air inlet assembly are spaced apart along a circumferential direction;

the plurality of air outlets on the air outlet assembly are spaced apart along the circumferential direction.

3. The diaphragm pump of claim 1, wherein the air inlet assembly includes a plurality of air inlets, the air outlet assembly includes a plurality of air outlets, and a count of the plurality of air inlets, a count of the plurality of air outlets, and a count of the plurality of shell plates are the same;

the air inlet holes located on the same shell plate are connected in parallel and then connected to a corresponding air inlet; and
the air outlet holes located on the same shell plate are connected in parallel and then connected to a corresponding air outlet.

4. The diaphragm pump of claim 1, wherein among the plurality of shell plates, the air inlet holes and the air outlet holes of the pump covers on one shell plate are connected in parallel or in series to form a first fluid line, and all the air outlet holes on the remaining shell plates are connected in parallel and then connected in series with the first fluid line.

5. The diaphragm pump of claim 1, wherein the plurality of shell plates include at least four shell plates, the at least four shell plates includes a first shell plate, a second shell plate, a third shell plate, and a fourth shell plate, the at least four shell plates are sequentially connected along the circumferential direction of the pump housing and together with the side plate enclose the pump chamber, and each of the at least four shell plates is provided with the chamber openings extending therethrough for communicating with the pump chamber;

the plurality of pump covers include a first pump cover and a second pump cover located on the first shell plate, a third pump cover and a fourth pump cover located on the second shell plate, a fifth pump cover and a sixth pump cover located on the third shell plate, and a seventh pump cover and an eighth pump cover located on the fourth shell plate, and each of the plurality of pump covers includes the air inlet hole and the air outlet hole;
wherein the air inlet hole of the first pump cover and the air inlet hole of the second pump cover are connected in parallel, the air inlet hole of the third pump cover and the air inlet hole of the fourth pump cover are connected in parallel, the air inlet hole of the fifth pump cover and the air inlet hole of the sixth pump cover are connected in parallel, and three parallel groups are connected to the air inlet assembly, respectively; the air outlet holes of the first pump cover, the second pump cover, the third pump cover, the fourth pump cover, the fifth pump cover, and the sixth pump cover are connected in parallel to form a first-stage fluid line, and the air inlet hole and the air outlet hole of the seventh pump cover and the air inlet hole and the air outlet hole of the eighth pump cover are connected to the first-stage fluid line in series, after being connected in parallel or in series with each other.

6. The diaphragm pump of claim 5, wherein the air inlet hole of the seventh pump cover and the air outlet hole of the seventh pump cover are connected in series to form a second-stage fluid line;

the air inlet hole of the eighth pump cover and the air outlet hole of the eighth pump cover are connected in series to form a third-stage fluid line; and
the second-stage fluid line is connected in series with the third-stage fluid line.

7. The diaphragm pump of claim 5, wherein each diaphragm structure includes:

a diaphragm body;
an outwardly turned flange, formed by bending and extending from a periphery of the diaphragm body along an axial direction of the diaphragm body;
wherein the diaphragm body and the outwardly turned flange are an integral structure, and an outer diameter of the integral structure is in a range of 104.5 mm to 105.5 mm;
the outwardly turned flange is configured to be inserted into the chamber opening, a width of the outwardly turned flange along a radial direction of the diaphragm body matches a width of the chamber opening, and the width of the outwardly turned flange along the radial direction of the diaphragm body is in a range of 4.2 mm to 5.25 mm.

8. The diaphragm pump of claim 5, wherein at least one of the air inlet assembly or the air outlet assembly is an interface structure;

the interface structure includes:
a cylindrical body, wherein the cylindrical body is provided with a through air hole extending therethrough along an axial direction thereof, one end of the through air hole is a closed end, and the other end of the through air hole is an open end; the cylindrical body is further provided with a plurality of branch air holes extending therethrough, the plurality of branch air holes are in communication with the through air hole, and the open end is connected to a fluid line.

9. The diaphragm pump of claim 8, wherein an inner wall of the open end is provided with an internal thread; or,

the cylindrical body is recessed inward at an outer wall surface of the open end to form a mounting step, the mounting step having a recessed wall surface proximate to the outer wall surface of the open end and a step surface connected to the recessed wall surface;
the interface structure further includes a clamping member, and the clamping member is sleeved on the recessed wall surface and supported on the step surface.

10. A pump chamber structure for a diaphragm pump, comprising:

a chamber body, wherein the chamber body is hollow and has a plurality of peripheral sidewalls sequentially connected along a circumferential direction of the chamber body, each of the plurality of peripheral sidewalls is provided with chamber openings, and the chamber openings on the two peripheral sidewalls disposed opposite to each other is arranged opposite to each other;
a plurality of pump covers, disposed to cover the plurality of chamber openings in a one-to-one correspondence;
a pump shaft, at least partially extending through the chamber body; and
a plurality of transmission components sequentially disposed within the chamber body along an axial direction of the pump shaft, wherein one end of each of the plurality of transmission components is rotatably connected to the pump shaft, and the other end of each of the plurality of transmission components is disposed to cover the corresponding chamber opening and collectively defines a working chamber together with the corresponding pump cover, and the plurality of transmission components are structurally identical.

11. The pump chamber structure of claim 10, wherein each transmission component includes:

an eccentric member, fixedly sleeved on an outer side of the pump shaft;
a bearing, sleeved on an outer side of the eccentric member;
a transmission rod, with one end sleeved on an outer peripheral side of the bearing; and
a diaphragm sheet, connected to the other end of the transmission rod and disposed to cover the corresponding chamber opening;
wherein the bearings of the plurality of transmission components are arranged side by side along the axial direction of the pump shaft; the two eccentric members of the two transmission components covering the two chamber openings disposed opposite to each other are formed integrally as a single piece; and the transmission rod is threadedly connected to the corresponding diaphragm sheet.

12. The pump chamber structure of claim 11, wherein the eccentric member includes a connecting post, an eccentric hole is eccentrically provided on the connecting post, the eccentric hole is sleeved on an outer peripheral side of the pump shaft, and the bearing is sleeved on an outer peripheral side of the corresponding connecting post.

13. The pump chamber structure of claim 11, wherein a plurality of chamber openings arranged along a same arc in the circumferential direction of the chamber body constitute a group of chamber openings, a plurality of transmission components correspondingly arranged with the same group of chamber openings constitute a group of transmission components, the plurality of transmission rods in the same group of transmission components are spaced apart along a circumferential direction of the pump shaft, and the plurality of transmission rods in the same group of transmission components are structurally identical and are each bent.

14. The pump chamber structure of claim 11, wherein a groove is provided around a periphery of the chamber opening, an engagement protrusion is provided on the diaphragm sheet, the engagement protrusion is engaged in the corresponding groove, and the pump cover is pressed against an outer side of the diaphragm sheet.

15. A pump chamber structure for a diaphragm pump, comprising:

a chamber housing, having a plurality of peripheral side surfaces, each of the plurality of peripheral side surfaces being provided with at least one chamber opening;
a pump shaft, disposed within the chamber housing along an axial direction of the chamber housing; and
a plurality of sets of connecting rod assemblies, arranged side by side within the chamber housing along the axial direction of the pump shaft, one end of each set of the plurality of sets of connecting rod assemblies being sleeved on an outer peripheral side of the pump shaft, and the other end of each set of the plurality of sets of connecting rod assemblies extending into the corresponding chamber opening;
wherein the chamber housing is provided with a plurality of limiting portions, an end of each set of the plurality of sets of connecting rod assemblies extending into the chamber opening is provided with a mating portion, and the limiting portion cooperates with the corresponding mating portion to limit movement of the corresponding connecting rod assembly along the axial direction of the pump shaft.

16. The pump chamber structure of claim 15, wherein each of the plurality of limiting portions includes a limiting groove disposed on a peripheral side of the chamber opening, the mating portion includes an engagement protrusion disposed at an end of the connecting rod assembly, and the engagement protrusion is in an engaged connection with the corresponding limiting groove to limit movement of the connecting rod assembly along the axial direction and the circumferential direction of the pump shaft.

17. The pump chamber structure of claim 16, wherein the limiting groove is a full-circumference annular groove disposed around the peripheral side of the corresponding chamber opening, and the engagement protrusion is a full-circumference annular protrusion; or, the engagement protrusion includes a plurality of protruding portions spaced apart along the circumferential direction of the chamber opening; or, the limiting groove includes a plurality of groove sections spaced apart along the circumferential direction of the chamber opening, the engagement protrusion includes the plurality of protruding portions spaced apart along the circumferential direction of the chamber opening, and the plurality of protruding portions are engaged in the plurality of groove sections in a one-to-one correspondence; or,

the engagement protrusion is the full-circumference annular protrusion.

18. The pump chamber structure of claim 16, wherein each set of the plurality of sets of connecting rod assemblies includes:

a connecting rod, wherein one end of the connecting rod is rotatably sleeved on an outer side of the pump shaft; and
a diaphragm sheet, wherein one end of the diaphragm sheet is connected to the other end of the connecting rod, and the other end of the diaphragm sheet extends into the corresponding chamber opening, the engagement protrusion is provided on the other end of the diaphragm sheet and is received in the limiting groove, so that the diaphragm sheet closes the chamber opening.

19. The pump chamber structure of claim 18, wherein the diaphragm sheet has a connecting end and a closed end disposed opposite to each other along a radial direction of the pump shaft, the connecting end is in threaded connection with the connecting rod, and a shape of the closed end matches a shape of the chamber opening; the chamber opening is circular, and the closed end is in a disk shape adapted to the chamber opening; the engagement protrusion is annularly provided at an edge of the closed end and protrudes from a side of the closed end facing the pump shaft.

20. The pump chamber structure of claim 18, wherein the pump chamber structure further comprises a plurality of pump covers connected to the chamber housing, the plurality of pump covers are disposed to cover a plurality of chamber openings in a one-to-one correspondence, and at least a portion of each of the plurality of pump covers is capable of extending into the chamber opening and being press-connected to the diaphragm sheet, so as to press-connect the engagement protrusion in the corresponding limiting groove.

Patent History
Publication number: 20260348376
Type: Application
Filed: Jul 14, 2026
Publication Date: Nov 5, 2026
Applicant: SUZHOU KERUIDA INTELLIGENT TECHNOLOGY CO., LTD. (Suzhou)
Inventors: Huiyong LIU (Suzhou), Haiming LIU (Suzhou), Yaping CHEN (Suzhou), Rongjun JU (Suzhou), Jiwei GUO (Suzhou)
Application Number: 19/740,307
Classifications
International Classification: F04B 53/16 (20060101); F04B 45/04 (20060101);